CN102448756A - Control device for hybrid vehicle - Google Patents

Control device for hybrid vehicle Download PDF

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Publication number
CN102448756A
CN102448756A CN2010800231650A CN201080023165A CN102448756A CN 102448756 A CN102448756 A CN 102448756A CN 2010800231650 A CN2010800231650 A CN 2010800231650A CN 201080023165 A CN201080023165 A CN 201080023165A CN 102448756 A CN102448756 A CN 102448756A
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CN
China
Prior art keywords
torque
motor vehicle
vehicle driven
mixed power
rotating machine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN2010800231650A
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Chinese (zh)
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CN102448756B (en
Inventor
菅野善仁
江渕弘章
北畠弘达
木村弘道
出盐幸彦
大野智仁
佐野英树
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Toyota Motor Corp
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Toyota Motor Corp
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Publication date
Priority claimed from JP2009127707A external-priority patent/JP4756396B2/en
Priority claimed from JP2009127703A external-priority patent/JP4586929B1/en
Application filed by Toyota Motor Corp filed Critical Toyota Motor Corp
Publication of CN102448756A publication Critical patent/CN102448756A/en
Application granted granted Critical
Publication of CN102448756B publication Critical patent/CN102448756B/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
    • B60K6/365—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings with the gears having orbital motion
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    • B60W20/00—Control systems specially adapted for hybrid vehicles
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    • B60K6/445—Differential gearing distribution type
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    • B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
    • B60K6/54—Transmission for changing ratio
    • B60K6/547—Transmission for changing ratio the transmission being a stepped gearing
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    • B60L15/00—Methods, circuits, or devices for controlling the traction-motor speed of electrically-propelled vehicles
    • B60L15/20—Methods, circuits, or devices for controlling the traction-motor speed of electrically-propelled vehicles for control of the vehicle or its driving motor to achieve a desired performance, e.g. speed, torque, programmed variation of speed
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    • B60L50/00—Electric propulsion with power supplied within the vehicle
    • B60L50/10—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines
    • B60L50/16—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines with provision for separate direct mechanical propulsion
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    • B60L50/00—Electric propulsion with power supplied within the vehicle
    • B60L50/50—Electric propulsion with power supplied within the vehicle using propulsion power supplied by batteries or fuel cells
    • B60L50/60—Electric propulsion with power supplied within the vehicle using propulsion power supplied by batteries or fuel cells using power supplied by batteries
    • B60L50/61—Electric propulsion with power supplied within the vehicle using propulsion power supplied by batteries or fuel cells using power supplied by batteries by batteries charged by engine-driven generators, e.g. series hybrid electric vehicles
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    • B60W10/00—Conjoint control of vehicle sub-units of different type or different function
    • B60W10/02—Conjoint control of vehicle sub-units of different type or different function including control of driveline clutches
    • B60W10/024—Conjoint control of vehicle sub-units of different type or different function including control of driveline clutches including control of torque converters
    • B60W10/026—Conjoint control of vehicle sub-units of different type or different function including control of driveline clutches including control of torque converters of lock-up clutches
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    • B60K1/00—Arrangement or mounting of electrical propulsion units
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    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
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    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/64—Electric machine technologies in electromobility
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/70—Energy storage systems for electromobility, e.g. batteries
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/7072—Electromobility specific charging systems or methods for batteries, ultracapacitors, supercapacitors or double-layer capacitors
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/72—Electric energy management in electromobility

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  • Combustion & Propulsion (AREA)
  • Power Engineering (AREA)
  • Automation & Control Theory (AREA)
  • Life Sciences & Earth Sciences (AREA)
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  • Hybrid Electric Vehicles (AREA)

Abstract

A hybrid vehicle in which changeover between a fixed gear ratio mode and a continuously variable gear ratio mode can be performed by the action of a locking mechanism, wherein generation of drag torque in this locking mechanism is detected. A hybrid vehicle (1) wherein a brake mechanism (400) is a wet-type multi-plate brake device, and is constructed so as to be capable of selectively locking a motor generator (MG1). If drag torque is generated in this brake mechanism (400) during a positive rotation state of (MG1), the actual (MG1) torque (Tg) (first torque) is larger (smaller in terms of reaction torque) than the torque (second torque) calculated from the operating condition of the hybrid vehicle (1) by the amount of the drag torque. If (MG1) is in a negative rotation state, the first torque is smaller than the second torque (larger in terms of reaction torque). The ECU (100) detects the drag torque by utilising this phenomenon.

Description

The control setup of motor vehicle driven by mixed power
Technical field
The present invention relates to possess the technical field of the control setup of the motor vehicle driven by mixed power that is used to carry out the lockout mechanism that speed change pattern switches.
Background technology
As this motor vehicle driven by mixed power, the type (for example with reference to patent documentation 1) that can lock electrical generator is arranged.According to patent documentation 1 disclosed motor vehicle driven by mixed power,, can reduce the timer-operated impact of lock through after the rotating speed that makes lockout mechanism is near zero, making its engaging again.
In addition, converter speed ratio pattern and stepless change have also been proposed to have fixedly than the scheme (for example with reference to patent documentation 2) of the motor vehicle driven by mixed power of pattern.
The prior art document
Patent documentation
Patent documentation 1: japanese kokai publication hei 9-156387 communique
Patent documentation 2: TOHKEMY 2004-345527 communique
Summary of the invention
As lockout mechanism, can be suitable for various snap fasteners, but in these snap fasteners, have that snap-fit element is not discharged fully when non-locking, produce a kind of type of losing torque that is called as drag torque.The generation of this drag torque is similar with a kind of fault in the lockout mechanism; But in the prior art that comprises the disclosed type of above-mentioned patent documentation; Do not consider the existence of this drag torque, the inevitable yet not related relevant open and enlightenment of technical conceive with the detection of this drag torque.
In addition; In the hybrid drive that makes rotating machine as the what is called rotation two degrees of freedom type of the antagonistic force elements act of combustion engine; No matter whether producing drag torque produces; All to adopt the structure that makes rotating machine converge on desired target rotational speed, therefore, have to detect according to the rotative speed of rotating machine simply in advance the existence of this drag torque.
That is, in the prior art, there is following technical matters:, in practice, also be difficult to detect exactly this drag torque even if produced drag torque.
The present invention makes in view of the above problems, and its problem is to provide the control setup of the motor vehicle driven by mixed power of the generation that can detect the drag torque in the lockout mechanism.
In order to solve above-mentioned problem, the control setup of motor vehicle driven by mixed power involved in the present invention is controlled motor vehicle driven by mixed power, and above-mentioned motor vehicle driven by mixed power possesses: dynamical element comprises rotating machine and combustion engine; Poewr transmission mechanism; Possess can mutual differential rotation a plurality of rotating elements, above-mentioned a plurality of rotating elements comprise can by first rotating element of above-mentioned rotating machine adjustment rotative speed, be connected with axle drive shaft that axletree links to each other on second rotating element and be connected the 3rd rotating element on the above-mentioned combustion engine; And lockout mechanism, can between lock-out state that can not rotate and the unlock state that can rotate, switch the state of above-mentioned first rotating element; Above-mentioned motor vehicle driven by mixed power constitutes with the mode of can be in stepless shift mode and fixedly switching speed change pattern between the speed change pattern; Wherein, under above-mentioned stepless shift mode, as the rotative speed of above-mentioned combustion engine and the converter speed ratio continuous variable of the ratio of the rotative speed of above-mentioned axle drive shaft, and the situation that is in above-mentioned unlock state with above-mentioned first rotating element is corresponding; Under the said fixing speed change pattern, above-mentioned converter speed ratio is fixed, and the situation that is in above-mentioned lock-out state with above-mentioned first rotating element is corresponding; The control setup of above-mentioned motor vehicle driven by mixed power is characterised in that the control setup of above-mentioned motor vehicle driven by mixed power possesses: operation condition is confirmed the unit, confirms the operation condition of above-mentioned dynamical element; And judging unit, this judging unit is judged having or not of drag torque in the above-mentioned lockout mechanism based on determined above-mentioned operation condition.
Motor vehicle driven by mixed power involved in the present invention is such vehicle, and it possesses at least: can be used as dynamical element for example power generator such as dynamotor and the rotating machine that constitutes that can supply with power to axle drive shaft; As the variety of way of its physics, machinery or electric formations such as the structure of the combustion system of the supply mode that can adopt irrelevant fuel classification, fuel, fuel, suction and discharge system and cylinder arrangement can be through fuel combustion generation power the combustion engine of machinery.
The control setup of motor vehicle driven by mixed power involved in the present invention is the control setup that following motor vehicle driven by mixed power is controlled, and for example can adopt following mode etc.: suitably comprise one or more CPU (Central Processing Unit), MPU (Micro Processing Unit), various treater or various controller or also further comprise various memory cell such as ROM (Read Only Memory), RAM (Random Access Memory), buffer memory or flash memory etc. and single or a plurality of ECU various processing units such as (Electronic Controlled Unit) of obtaining; Various computer systems such as various controllers or micro computer device.
Motor vehicle driven by mixed power involved in the present invention possesses Poewr transmission mechanism.Poewr transmission mechanism is following mechanism; Promptly; Possess a plurality of rotating elements that can form differential action each other; Comprise first rotating element that is connected directly or indirectly with rotating machine and can adjusts the rotative speed that produces by rotating machine, with axle drive shaft bonded assembly second rotating element and with combustion engine bonded assembly the 3rd rotating element; Under above-mentioned differential action, corresponding with the state (just comprise and can rotate and whether be in and other rotating elements or retaining element bonded assembly state etc.) of each rotating element, carry out the various transmission of powers (transmission of torque just) between above-mentioned dynamical element and the axle drive shaft.
Among a plurality of rotating elements that Poewr transmission mechanism possessed first, second and the 3rd rotating element; Constitute the binary modified roll mechanism of rotation; If wherein the rotative speed of two elements is definite all the time or selectively, the rotative speed of a then remaining rotating element also is determined (the included rotating element of this modified roll mechanism also needn't be defined in this element in addition) naturally.Therefore, the antagonistic force element that rotating machine can be used as the cooresponding reaction force torque of torque of burden and combustion engine plays a role, and the rotative speed control unit that also can be used as combustion engine plays a role.
Motor vehicle driven by mixed power involved in the present invention possesses can adopt the for example lockout mechanism of variety of ways such as wet multi-plate brake equipment, clutch equipment or electromagnetism cam lock fixed pattern clutch equipment; This lockout mechanism can switch the state of first rotating element between non-rotatable lock-out state and rotatable unlock state; Wherein, Under above-mentioned lock-out state; Non-rotatably be fixed in the regulation retaining element through for example physics, machinery, various engaging power electric or magnetic force, under above-mentioned unlock state, do not receive the influence of the related engaging power of this lock-out state at least.In motor vehicle driven by mixed power involved in the present invention, form following structure, this lock-out state and unlock state are respectively with corresponding as the fixedly speed change pattern and the stepless shift mode of different each other speed change patterns.
Stepless shift mode is following speed change pattern; Promptly; In the binary modified roll mechanism of above-mentioned rotation; Through rotating machine is played a role (promptly first rotating element is necessary for unlock state) as the rotative speed control unit of combustion engine, the rotative speed that can make combustion engine and the ratio of the rotative speed of axle drive shaft be converter speed ratio in theory, in fact or (step-wise manner that also comprises in the practice Yu be equal to continuously) variation continuously in the physics of predesignating, machinery, mechanism or the electric restriction scope.In this case; As an optimal way; The operating point of the combustion engine point of an operating condition of the regulation combustion engine of combustion engine rotative speed and torque defined (for example by) for example in theory, in fact perhaps freely select in any restriction scope; For example, be controlled to specific consumption of fuel in theory, in fact perhaps in any restriction scope the minimum or system effectiveness of motor vehicle driven by mixed power (combined efficiency of for example calculating) based on the transmission efficiency of Poewr transmission mechanism and the heat efficiency of combustion engine etc. in theory, the in fact perhaps best burnup operating point of maximum etc. in any restriction scope.Poewr transmission mechanism can adopt the gear mechanism of one or more sun and planet gear etc. as an optimal way; Comprising under the situation of a plurality of sun and planet gears, can suitably have the part of the rotating element that constitutes each sun and planet gear at a plurality of sun and planet gears each other.
Fixedly speed change pattern is following speed change pattern, that is, likewise in the binary modified roll mechanism of rotation, realize through first rotating element is maintained in the lock-out state that can not rotate, and uniquely stipulates above-mentioned converter speed ratio accordingly.Promptly; Under the situation that first rotating element is in the lock state; According to the rotative speed of rotative speed of this first rotating element (promptly zero) and second rotating element of representing the speed of a motor vehicle and unique cooresponding slew mode, unique rotative speed of stipulating remaining the 3rd rotating element accordingly.At this moment; If the direct coupled structure of first rotating element and rotating machine; Then rotating machine becomes zero rotating speed; Realization is called as the state of so-called MG1 locking, if first rotating element via other rotating elements that have differential relation each other and rotating machine bonded assembly structure, then the rotative speed of rotating machine be fixed as corresponding to these gears than and a definite value.For the latter, can suitably realize the state that is called as so-called O/D locking of rotative speed of the not enough axle drive shaft of rotative speed of combustion engine.In a word, fixedly speed change pattern can suitably be selected, to avoid producing the electric route of the low efficiency that makes the hybrid drive single-piece system effectiveness reduction that comprises dynamical element and Poewr transmission mechanism that is called as power cycle.
On the other hand, lockout mechanism involved in the present invention structurally can adopt the intermediateness that becomes above-mentioned lock-out state and unlock state, the state (following suitably be called " intermediateness ") that first rotating element does not discharge from retaining element fully.Under such intermediateness, first rotating element to accept the drag torque as a certain braking torque in various degree, becomes the state how many its rotations is hindered from retaining element fixing under lock-out state.This drag torque is the major cause that can reduce to the axle drive shaft torque transmitted, in other words, is the major cause that the system effectiveness of hybrid drive is reduced as the loss torque.The existence of such drag torque in view of the effect of the lockout mechanism that originally can carry with efficiently the turning to purpose of hybrid drive, is very unfavorable.
So, in the control setup of motor vehicle driven by mixed power involved in the present invention, as following, detect the drag torque (promptly acting on the drag torque of first rotating element) in the lockout mechanism.That is, according to the control setup of motor vehicle driven by mixed power involved in the present invention, when it moves, confirm that by operation condition the unit confirms the operation condition of dynamical element, judging unit is judged having or not of this drag torque based on determined this operation condition.
At this; In Poewr transmission mechanism; Constructed differential relation each other each other at rotating element; Act on the drag torque of first rotating element, the rotating machine that not only the rotative speed adjustment unit as first rotating element is played a role also possibly impact being connected to the operation condition that has a combustion engine on the 3rd rotating element of differential relation with first rotating element.More specifically; Be used to keep be connected to and have the desired rotative speed of axle drive shaft or the operation condition of needed rotating machine of torque or combustion engine on second rotating element of differential relation, according to having or not of this drag torque and inevitable different with them.
Saidly confirm unit determined " operation condition of dynamical element " by operation condition; Just refer in advance to be confirmed as the exercises condition that might produce significant difference, for example comprise the intensity of variation etc. of the rotative speed of the torque, rotating machine or the combustion engine that are used to keep a needed rotating machine of rotative speed according to having or not of drag torque based on experiment, experience, theoretical or simulation etc.
Therefore, judging unit can suitably be judged to have or not the generation drag torque based on this rotating machine or the operation condition of combustion engine.That is,, can detect the drag torque in the lockout mechanism according to the control setup of motor vehicle driven by mixed power involved in the present invention.
As supplemental instruction; The present invention realizes the accurate detection of drag torque according to following technical conceive: the essentiality that this drag torque is detected is expected seeing that the drag torque in the lockout mechanism can make the situation of the system effectiveness of motor vehicle driven by mixed power in practice in (1); (2) pay close attention to having or not of this drag torque can give have differential relation with first rotating element and with it the 3rd rotating element respectively the operation condition of bonded assembly rotating machine and combustion engine bring the such aspect of significant difference; (3) based on above-mentioned focus, the operation condition that utilizes these rotating machines and combustion engine is as the desired value that is used to detect drag torque.
Therefore; Any technical conceive with respect to the existence that reckons without this drag torque; Even in addition also with respect to the existence of having considered drag torque but do not comprise yet with its detection essentiality with and specifically detect any technical conceive of the relevant enlightenment of gimmick; Reliable Detection is carried out in generation to drag torque; For example can take the generation of drag torque is informed chaufeur, impelled chaufeur to use fair game or with useful countermeasure in practice such as the controlled condition optimization of motor vehicle driven by mixed power, advantage is tangible at that point.
In a mode of the control setup of motor vehicle driven by mixed power involved in the present invention; The torque that above-mentioned operation condition is confirmed to confirm above-mentioned rotating machine according to the controlling quantity of above-mentioned rotating machine in the unit is as first torque; This first torque is as an above-mentioned operation condition; And; The torque of confirming above-mentioned rotating machine according to the operating condition of the above-mentioned motor vehicle driven by mixed power relevant with the torque of above-mentioned rotating machine is as second torque, and this second torque is as another above-mentioned operation condition, and above-mentioned judging unit is judged having or not of above-mentioned drag torque based on determined above-mentioned first torque and above-mentioned second torque.
According to this mode; Operation condition is confirmed the unit, the first, according to the controlling quantity (for example various drive conditions such as target torque or drive current, driving voltage or driving electric etc.) of rotating machine; Confirm the torque of rotating machine, as i.e. first torque of an operation condition of dynamical element; The second, according to the operating condition of predesignating the motor vehicle driven by mixed power relevant (for example require output or require torque etc.), confirm the torque of rotating machine, as i.e. second torque of other operation conditions of dynamical element with the torque of rotating machine.That is, as performance qualitatively, the torque (i.e. second torque) under the normal circumstances that operation condition is confirmed to confirm that actual torque of rotating machine (i.e. first torque) and rotating machine have originally in the unit.
The actual torque of first torque and rotating machine is of equal value; Second torque be rotating machine desirable or theoretical target torque (actual target torque since be used for rotative speed with rotating machine be maintained in target rotational speed rotation F/B control etc. influence and suitably change); So; In lockout mechanism, do not produce under the normal condition of drag torque, both possibilities consistent or unanimous on the whole are high; On the contrary, if in lockout mechanism, produced drag torque, then both deviate from each other.If utilize this phenomenon, then can suitably judge the generation of drag torque.
At this; In the combustion engine; The for example corresponding fired state that influenced by various controlled conditions such as engine temperature, fuel injection amount, fuel injection timing and point of ignition; Actual torque and target torque deviate from easily etc., with the rotating machine easy step-down of control accuracy of torque/mass ratio mutually, and also likewise become the major cause that causes first torque and second torque to deviate from drag torque in the cogging (deviating from of target torque and actual torque) of this internal combustion engine side generation.
Yet the change because of first torque that situation produced (being the actual torque of rotating machine) of such internal combustion engine side can not change according to the hand of rotation (being positive veer or clockwise sence) of rotating machine.Promptly; To increasing under the side out-of-position situation, becoming, littler (if the torque that will act on the direction identical with the torque of combustion engine is made as positive torque, then reaction force torque is negative torque in the torque of combustion engine; Be that bigger it is more little for absolute value); And in the torque of combustion engine to reducing under the side out-of-position situation, bigger (that is, reaction force torque reduces) becomes.On the other hand; Drag torque is owing to always act on the direction of the rotation that stops first rotating element; So, in lockout mechanism, producing under the situation of drag torque, drag torque is given hand of rotation according to rotating machine of influence that first torque brings and different.
Therefore,, the deviation and the drag torque of the torque of internal combustion engine side can be distinguished, drag torque can be detected exactly according to this mode.
In addition, in this mode, above-mentioned judging unit also can constitute as follows; When above-mentioned rotating machine is in when just changeing state; Under the big situation of determined above-mentioned second torque of determined above-mentioned first torque ratio, and, when above-mentioned rotating machine is in negative commentaries on classics state; Under the little situation of above-mentioned second torque of determined above-mentioned first torque ratio, above-mentioned judging unit is judged as respectively and produces above-mentioned drag torque.
Under the situation that produces drag torque; If rotating machine is for just changeing state; Effect has drag torque on the direction identical with reaction force torque; Thereby the absolute value of needed reaction force torque diminishes, and first torque becomes big with respect to second torque (promptly the normal circumstances that does not produce drag torque should from the torque of rotating machine output).On the other hand, if rotating machine is negative commentaries on classics state, the direction that direction and drag torque acted on that reaction force torque acted on is opposite sense each other, thereby the absolute value of reaction force torque becomes the amount of big drag torque, and first torque diminishes with respect to second torque.Therefore, judging unit can detect exactly the generation of drag torque according to such judgment standard.
In other modes of the control setup of motor vehicle driven by mixed power involved in the present invention; Above-mentioned operation condition confirm the unit confirm at least one side in above-mentioned rotating machine and the above-mentioned combustion engine to the convergence state of target rotational speed convergence as above-mentioned operation condition, above-mentioned judging unit is judged having or not of above-mentioned drag torque based on the above-mentioned convergence state of confirming.
Under the situation that produces drag torque; The rotating machine of following the operating condition variation of motor vehicle driven by mixed power and producing or the convergence state to the target rotational speed convergence of combustion engine (just refer to convergence rate or convergence time etc.; But also can be cambic time waveform etc. up to convergence), compare to some extent with the convergence state under the normal circumstances that does not produce drag torque and to change.Therefore, according to this mode, can detect drag torque exactly based on this convergence state.
In other modes of the control setup of motor vehicle driven by mixed power involved in the present invention; The control setup of above-mentioned motor vehicle driven by mixed power also possesses first control unit; This first control unit is controlled above-mentioned rotating machine with the mode that reduces with the cooresponding counter-force torque of the torque of above-mentioned combustion engine during stable the going of above-mentioned motor vehicle driven by mixed power; Above-mentioned operation condition confirm that the unit is confirmed to follow above-mentioned counter-force torque to reduce and the variable quantity of the rotative speed of the above-mentioned combustion engine that produces as above-mentioned operation condition, above-mentioned judging unit is judged having or not of above-mentioned drag torque based on the variable quantity of the rotative speed of the determined above-mentioned above-mentioned combustion engine of following above-mentioned counter-force torque to reduce and producing.
Under the situation that reaction force torque is reduced, by the mutual differential action of rotating element the rotative speed of combustion engine is risen, related variable quantity changes according to having or not of drag torque to some extent but this rotative speed rises.According to this mode, owing to the variable quantity based on the rotative speed of the combustion engine of following this reaction force torque to reduce to produce is judged having or not of drag torque, so, can detect drag torque exactly.
In addition, the variation of the rotative speed when reaction force torque is reduced, with before described first and the interrelation of second torque same, on the hand of rotation of rotating machine, be affected.That is, if rotating machine is for just changeing state, the rising of the rotative speed of the combustion engine when reaction force torque is reduced is compared with normal circumstances, the amount of drag torque that amplitude is little; On the other hand, if rotating machine is negative commentaries on classics state, the rising of the rotative speed of combustion engine compare with normal circumstances amplitude big the amount of drag torque.Therefore, ideal when judgment unit judges has or not the generation drag torque, is preferably grasped the hand of rotation of rotating machine.But; Even if the hand of rotation of rotating machine has skew; The rotative speed that makes combustion engine by drag torque change aspect do not change yet; Only with regard to the detection of drag torque, if can be in advance based on experiment, experience, theoretical or virtually wait the movement of grasping the combustion engine under the normal circumstances, just needn't grasp the hand of rotation of rotating machine.
In other modes of the control setup of motor vehicle driven by mixed power involved in the present invention; The variable quantity of the rotative speed of the above-mentioned combustion engine when above-mentioned operation condition confirms that starting is confirmed in the unit is as above-mentioned operation condition, and the variable quantity of the rotative speed of the above-mentioned combustion engine of above-mentioned judging unit during based on determined above-mentioned starting is judged having or not of above-mentioned drag torque.
According to this mode, capable of usingly can make the engine starting this point by rotating machine, drag torque is detected.Therefore, can increase the detection frequency of drag torque.
In addition, the variable quantity of the rotative speed when such starting, with before described first and the interrelation of second torque same, be affected at the rotary area of rotating machine.Promptly; Motor vehicle driven by mixed power for example is employed in the structure that connects other rotating machines on the axle drive shaft; Can undertaken except in the vehicle stopped process, requiring cranking internal combustion engine, in vehicle ', also can requiring cranking internal combustion engine under the situation that so-called EV goes by above-mentioned other rotating machines.When the vehicle halted state is started, rotating machine is in just changes state, and when vehicle running state starts, rotating machine is in the negative zone of changeing.Therefore, under the situation that produces drag torque, for the former, the part of starting torque is offset by drag torque, and actual starting torque reduces, and it is slow that the variation of the rotative speed of combustion engine becomes.On the other hand, for the latter, become the form that starting torque is assisted by drag torque, so actual starting torque increases on the contrary, it is big that the variation of the rotative speed of combustion engine becomes.
Therefore, it is desirable to, when judgment unit judges has or not the generation of drag torque; The preferred hand of rotation of grasping rotating machine; Even and if the hand of rotation of rotating machine skew, the rotative speed of the combustion engine when being made starting by drag torque changes and does not also change on this point, only with regard to the detection of drag torque; As long as can grasp the movement of the combustion engine under the normal circumstances in advance based on experiment, experience, theoretical perhaps simulation etc., just needn't grasp the hand of rotation of rotating machine.
In other modes of the control setup of motor vehicle driven by mixed power involved in the present invention; The control setup of above-mentioned motor vehicle driven by mixed power possesses: side-play amount is confirmed the unit; Be judged as under the situation that produces above-mentioned drag torque; The operation condition of the above-mentioned dynamical element of confirming to cause because of above-mentioned drag torque is with respect to the side-play amount of the operation condition under the normal circumstances; With second control unit, corresponding determined above-mentioned side-play amount is controlled the starting torque of above-mentioned combustion engine and at least one side who reduces in the torque.
According to this mode; Confirm the side-play amount of the operation condition of the dynamical element that the unit is confirmed to cause because of drag torque by side-play amount, by the corresponding determined above-mentioned side-play amount of second control unit to starting torque and/or reduce torque (torque when promptly, combustion engine being stopped) and control.Therefore, when the starting of combustion engine or when stopping, can preventing the overlong time that causes the rotative speed of combustion engine to be detained because of drag torque from can suppress Vehicular vibration effectively in resonance bands.
As operation condition; Confirm at least one side's in rotating machine and the combustion engine convergence state to target rotational speed; In a mode of the control setup of motor vehicle driven by mixed power involved in the present invention; Possess: the 3rd control unit, under the state of having selected above-mentioned stepless shift mode, with the rotative speed of above-mentioned rotating machine mode to above-mentioned target rotational speed convergence; The rotative speed of corresponding above-mentioned rotating machine and the deviation of above-mentioned target rotational speed are controlled the torque of above-mentioned rotating machine; With calculate the unit, the inertia torque value that produces because of the inertia of the rotatory inertia system that comprises above-mentioned dynamical element during the above-mentioned rotating machine of the torque value of feedback of the above-mentioned rotating machine of calculating when being based on the above-mentioned rotating machine of corresponding above-mentioned deviation control and corresponding above-mentioned deviation control is calculated above-mentioned drag torque.
Under the state of having selected stepless shift mode, carry out the rotative speed controlled reset of rotating machine by control unit.That is, in this rotative speed controlled reset, with the mode that the rotative speed of rotating machine is restrained to target rotational speed, the rotative speed of corresponding above-mentioned rotating machine and the deviation of target rotational speed are controlled the torque of rotating machine.At this moment, the target rotational speed of rotating machine is by setting with the cooresponding form of the target operating point of combustion engine.Though the target torque of rotating machine confirms that according to the differential action of the rotating element in the Poewr transmission mechanism and the gear ratio between corresponding and rotating element it becomes the ideal value under the stabilized conditions.
On the other hand; Comprising just from the fixing transition period of speed change pattern after the stepless shift mode switching; At the rotative speed of rotating machine (in first rotating element and rotating machine bonded assembly structure; Initial value is zero) in the process that target rotational speed rises, need the inertia (rotatory inertia) of dynamical element be compensated.That is, if do not take any countermeasure, then the part of the torque of rotating machine can be offset by this inertia torque, and the shaft torque of rotating machine reduces.The shaft torque of rotating machine is the reaction force torque of the torque of combustion engine just, and it reduces to cause the reducing of output torque of axle drive shaft.Therefore, for fear of the reducing and make rotating machine of this axle drive shaft torque, need the inertia torque of dynamical element be compensated rapidly and exactly to the target rotational speed convergence.
Thereby, when control unit is rotated the rotative speed controlled reset of motor, according to the deviation of the above-mentioned rotative speed of correspondence and definite torque value of feedback is revised the torque of rotating machine.Torque according to the revised rotating machine of this torque value of feedback; Be by confirming with desired torque of confirming according to the target torque of above-mentioned combustion engine or the different system of reference torque; Can be described as the actual torque of rotating machine, both converge under the state of target rotational speed balance ideally at the rotative speed of rotating machine.
So, in this mode,, as following, infer the drag torque (promptly, acting on the drag torque of first rotating element) in the lockout mechanism by calculating the unit.Promptly; Calculate the value of feedback of the above-mentioned rotating machine torque of being calculated when the unit is based on corresponding above-mentioned deviation control rotating machine and when the above-mentioned rotating machine of the above-mentioned deviation control of correspondence because of the value of the inertia torque that inertia produced (above-mentioned inertia torque) of the rotatory inertia system that comprises dynamical element, calculate the drag torque in the lockout mechanism.
As above-mentioned, when rotating machine being carried out the rotative speed controlled reset by control unit, the feedback of the cooresponding torque of deviation of formation and rotative speed.The related torque value of feedback of this torque feedback is the inertia torque of compensation rotatory inertia system basically; And in lockout mechanism, produce under the situation of drag torque; This drag torque can hinder the rotation of rotating machine on acting on the direction opposite with the torque of rotating machine the time; Can assist the rotation of rotating machine in the time of on acting on equidirectional, bring influence can in a word the slew mode of rotating machine.
On the other hand, the inertia torque about the rotatory inertia that comprises dynamical element is as if having grasped the inertia that rotatory inertia is based on experiment, experience, theoretical perhaps simulation etc. in advance, then needs only and confirms that rotative speed just can unique derivation accordingly.This inertia torque and and the cooresponding torque of torque value of feedback between produce under the situation of significant difference, can regard that the chances are as and cause because of the drag torque of lockout mechanism.Therefore, the result who for example obtains as deducting the opposing party from a side etc. calculate the unit and can calculate drag torque exactly.
In a mode of the control setup that possesses the motor vehicle driven by mixed power involved in the present invention of calculating the unit, also possesses the identifying unit of judging the state of above-mentioned lockout mechanism based on the above-mentioned drag torque of being calculated.
In view of can the drag torque of calculating being used for the condition judgement of lockout mechanism by calculating the structure that drag torque is calculated in the unit.Which kind of mode the practice mode of the judgement that identifying unit is related is not limited to, and no matter via any judgment processing, according to this mode, also can the drag torque of calculating suitably be used in the suitable utilization of motor vehicle driven by mixed power.In addition, identifying unit for example both can be judged the lockout mechanism fault when the drag torque of calculating is zero, also can judge the lockout mechanism fault under for the situation more than the fixing or variable threshold value in the drag torque of calculating.
In addition, in this mode, above-mentioned identifying unit can be to be judged to be above-mentioned lockout mechanism under the situation more than the specified value to be in faulty condition in the above-mentioned drag torque of being calculated also.
In this case, can carry out lockout mechanism more easily and be in the such judgement of faulty condition, be favourable aspect the control load of identifying unit.In addition, said " faulty condition " is meant the state of stipulating in order the time to distinguish in control, might not only represent the state that the action of lockout mechanism significantly is restricted.For example, also can be simply from informing the so smaller state of chaufeur to requiring to keep out of the way rapidly the more serious state like this that goes, the setting situation of value is carried out variable control to the implication of putting into practice shown in the faulty condition according to the rules.
In other modes of the control setup that possesses the motor vehicle driven by mixed power involved in the present invention of calculating the unit, also possesses the amending unit that the corresponding above-mentioned drag torque of being calculated is revised the output torque of above-mentioned axle drive shaft.
In the binary modified roll mechanism of aforesaid rotation in Poewr transmission mechanism, cut apart through torque among the torque of combustion engine, calculated according to the reaction force torque of rotating machine to axle drive shaft.Therefore; If being embodied in shaft torque on the actual axle that is connected with rotating machine comprises drag torque and makes and produce difference between actual torque and the through torque from rotating machine output; Then the precision of inferring of through torque reduces, and the axle drive shaft torque is with respect to the required value change.
At that point; According to this mode; Owing to revise the output torque of axle drive shaft according to the drag torque of calculating through amending unit; So can the axle drive shaft torque be maintained all the time and require torque, suitably suppress because of the Vehicular vibration that cogging caused of axle drive shaft or the reduction of power-handling capability.
In other modes of the control setup that possesses the motor vehicle driven by mixed power involved in the present invention of calculating the unit, also possesses the selected cell of selecting the side in above-mentioned stepless shift mode and the said fixing speed change pattern based on the above-mentioned drag torque of being calculated.
According to this mode, owing to can select stepless shift mode and the fixing side among the speed change pattern, so can avoid keeping out of the way burnup or the reduction of efficient when going at motor vehicle driven by mixed power based on the drag torque of calculating.
In addition, in this mode, above-mentioned selected cell also can be selected the high side of system effectiveness among above-mentioned stepless shift mode and the said fixing speed change pattern, above-mentioned motor vehicle driven by mixed power.
Like this,, can relax the influence of the loss that causes because of drag torque as much as possible, motor vehicle driven by mixed power is kept out of the way efficiently gone through system effectiveness is selected speed change pattern as judge index.
In other modes of the control setup that possesses the motor vehicle driven by mixed power involved in the present invention of calculating the unit, above-mentioned motor vehicle driven by mixed power also possess can with above-mentioned axle drive shaft between carry out power input and output and other rotating machines different with above-mentioned rotating machine.
According to this mode, even the part that is embodied in axle drive shaft in the torque of combustion engine is with respect to requiring under the not enough situation of torque, also can be through assisting to keep and require torque from the torque of other propulsions source.And, satisfying under the situation of regulation permissive condition etc., also can only make motor vehicle driven by mixed power carry out so-called EV and go through power supply from other propulsions source, in practice, be useful.
Effect of the present invention and other advantages can be known by the embodiment of following explanation.
Description of drawings
Fig. 1 is the summary pie graph that schematically illustrates the structure of the related motor vehicle driven by mixed power of first embodiment of the present invention.
Fig. 2 is the summary pie graph that schematically illustrates the structure of the hybrid drive in the motor vehicle driven by mixed power of Fig. 1.
Fig. 3 is the mode chart that a section of the driving engine that hybrid drive possessed of illustrated view 2 constitutes.
Fig. 4 is the action alignment chart of operation condition of each several part of the hybrid drive of instruction diagram 2.
Fig. 5 is that the drag torque of in the motor vehicle driven by mixed power of Fig. 1, being carried out by ECU detects the diagram of circuit of controlling.
Fig. 6 is the action alignment chart of hybrid drive of a method of inspection of the drag torque of the lockout mechanism in the motor vehicle driven by mixed power of instruction diagram 1.
The figure of the time lapse of the rotative speed of the MG1 when other method of inspections, the illustration MG1 locking that Fig. 7 relates to the drag torque in the lockout mechanism is carried out.
Fig. 8 relates to other method of inspections, the illustration reaction force torque of the drag torque in the lockout mechanism and hangs down the figure of the time lapse of the combustion engine rotative speed Ne when subtracting.
Combustion engine rotative speed Ne when Fig. 9 relates to other method of inspections, the illustration starting of the drag torque in the lockout mechanism with and the figure of the time lapse of variation delta Ne.
Figure 10 is the summary pie graph that schematically illustrates the structure of the related hybrid drive of second embodiment of the present invention.
Figure 11 is the summary pie graph that schematically illustrates the structure of the hybrid drive in the related motor vehicle driven by mixed power of the 3rd embodiment of the present invention.
Figure 12 is the mode chart that a section of the lockout mechanism that hybrid drive possessed of illustration Figure 11 constitutes.
Figure 13 is the mode chart that is illustrated in a section formation of the lockout mechanism of watching to arrow line A direction among Figure 12.
To be explanation make the mode sectional drawing of sun gear from release position to the lock-out state transforming process by the locking action of the stop mechanism of Figure 12 to Figure 14.
Figure 15 is the diagram of circuit of the variable speed control in the motor vehicle driven by mixed power of Fig. 1, carried out by ECU.
Figure 16 is the basic controlling block scheme of stepless shift mode.
Figure 17 is the control block scheme of selected stepless shift mode in the variable speed control of Figure 15.
Figure 18 is the action alignment chart of the hybrid drive of Figure 11.
Figure 19 is the summary pie graph that schematically illustrates the structure of the related hybrid drive of the 4th embodiment of the present invention.
The specific embodiment
< working of an invention mode >
Followingly suitable various embodiments of the present invention are described with reference to accompanying drawing.
< first embodiment >
< structure of embodiment >
At first the structure of the related motor vehicle driven by mixed power 1 of first embodiment of the present invention is described with reference to Fig. 1.At this, Fig. 1 is the summary pie graph that schematically illustrates the structure of motor vehicle driven by mixed power 1.
In Fig. 1; Motor vehicle driven by mixed power 1 possesses ECU100, PCU (Power Control Unit) 11, battery 12, accelerator open degree sensor 13 and car speed sensor 14 and also has hybrid drive 10, is an example of " motor vehicle driven by mixed power " involved in the present invention.
ECU100 is the electronic control unit that possesses CPU (Central Processing Unit), ROM (Read Only Memory) and RAM etc., constitutes the action of the each several part that can control motor vehicle driven by mixed power 1, is an example of " control setup of motor vehicle driven by mixed power " involved in the present invention.The drag torque that ECU100 states after constituting and can carrying out according to the control program that is stored in ROM detects control.In addition; ECU100 constitutes as " operation condition is confirmed the unit " involved in the present invention, " judging unit ", " first control unit ", " side-play amount is confirmed the unit " and " second control unit " electronic control unit of the one that plays a role of an example separately, constitutes the related separately action of these mechanisms and is all carried out by ECU100.But; These mechanisms involved in the present invention physics, machinery and electric structure separately is not limited thereto, and for example these mechanisms also can be used as formations such as various computer systems such as a plurality of ECU, various processing unit, various controller or micro computer device separately.
PCU11 is following control unit; Promptly; Comprise and constitute and to change the direct current (DC) that obtains from battery 12 into alternating current and the dynamotor MG1 that states backward and dynamotor MG2 supplies with and will be changed into the not shown inverter that direct current (DC) is supplied with to battery 12 by the alternating current that dynamotor MG1 and dynamotor MG2 generating obtain; Constitute and to control the input and output (that is, between each dynamotor, not carrying out supply, the acceptance of electric power in this case each other) of the mutual electric power of the input and output of the electric power between battery 12 and each dynamotor or each dynamotor via battery 12 ground.PCU11 is electrically connected with ECU100, is the structure by its action of ECU100 control.
Battery 12 is to constitute the chargeable electricity accumulating unit that can conduct plays a role with the relevant electric power supply source of electric power that is used for power operation dynamotor MG1 and dynamotor MG2.
Accelerator open degree sensor 13 is that the operational ton that constitutes the not shown acceleration pedal that can detect motor vehicle driven by mixed power 1 is the sensor of accelerator open degree Ta.Accelerator open degree sensor 13 forms following structure, and it is electrically connected with ECU100, and presses the constant or inconstant cycle with reference to detected accelerator open degree Ta by ECU100.
Car speed sensor 14 is the sensors that constitute the speed V that can detect motor vehicle driven by mixed power 1.Car speed sensor 14 forms following structure, and it is electrically connected with ECU100, and presses the constant or inconstant cycle with reference to detected speed V by ECU100.
Hybrid drive 10 is power units that the dynamic assembly as motor vehicle driven by mixed power 1 plays a role.At this,, the concrete formation of hybrid drive 10 is described with reference to Fig. 2.At this, Fig. 2 is the summary pie graph that schematically illustrates the structure of hybrid drive 10.In addition, in the figure, the position with Fig. 1 repetition is marked identical Reference numeral and suitably omits its explanation.
In Fig. 2, hybrid drive 10 possesses driving engine 200, power division mechanism 300, dynamotor MG1 (following suitably abbreviate as " MG1 "), dynamotor MG2 (following suitably abbreviate as " MG2 "), stop mechanism 400, input shaft 500, axle drive shaft 600 and speed reduction gearing 700.
Driving engine 200 is that an example of " combustion engine " involved in the present invention is an engine petrol, and the major impetus source that constitutes as motor vehicle driven by mixed power 1 plays a role.At this,, describe with regard to the concrete formation of driving engine 200 with reference to Fig. 3.At this, Fig. 3 is the mode chart that a section of illustration driving engine 200 constitutes.In addition, in the figure, the position with Fig. 1 and Fig. 2 repetition is marked identical Reference numeral and suitably omits its explanation.In addition; " combustion engine " among the present invention is such notion; Promptly; For example comprise two circulations or the four formula driving engine etc. that moves in circles, have at least one cylinder, comprise the machinery that the power that produced can be with the mixed gas burning that in the combustion chamber of this cylinder internal, comprises various fuel such as gasoline, light oil or ethanol for example the time is suitably taken out as propulsive effort via the physics or the mechanical transfer mechanism of for example piston, pipe link and bent axle etc.As long as satisfy this notion, the structure of combustion engine involved in the present invention is not limited to the structure of driving engine 200, can have variety of way.
In Fig. 3; Driving engine 200; In cylinder 201; Be exposed to the igniting action that the ignition device 202 in the combustion chamber carried out through a part and make mixed gas burning, and it is rotatablely moving of bent axle 205 that the crank motion of the piston 203 that produces corresponding to this burns formed force of explosion can change internal combustion engine output shaft into via pipe link 204 by light-up plug (omission Reference numeral).
Near bent axle 205, the crank position sensor 206 of the position of rotation (being crankshaft angle) that detects bent axle 205 is set.This crank position sensor 206 is electrically connected with ECU100 (not shown), in ECU100, forms based on calculating the structure of the combustion engine rotative speed NE of driving engine 200 from the crank angle signal of these crank position sensor 206 outputs.
In addition, driving engine 200 is in the four-banger of connecting that forms with vertical four cylinders 201 of direction arranged in series of paper, because the structure of each cylinder 201 is equal to each other, so in Fig. 2, only describe with regard to a cylinder 201.In addition; The number of cylinders in the combustion engine involved in the present invention and the arrangement mode of each cylinder are not limited to the mode of driving engine 200 in satisfying the scope of above-mentioned notion; Can take multiple mode; For example both can be six cylinders, eight cylinders or 12 cylinder engines, also can be V-type, flat opposed type etc.
In driving engine 200, through aspirate tube 207 and via air suctiton inlet 210,, air suction valve 211 is directed to cylinder 201 inside when driving valve from outside suction air.On the other hand, expose the fuel injection valve of eductor 212 at air suctiton inlet 210, formation can be with respect to the structure of air suctiton inlet 210 burner oils.Mix with aspirated air before and after the duration of valve opening of air suction valve 211 from eductor 212 injected fuel, form above-mentioned miscellaneous gas.
Bunkering forms the structure that is fed into eductor 212 through the effect of not shown charge pump via not shown distribution pipe in not shown Fuel Tank.Become exhaust at cylinder 201 internally fired miscellaneous gass, when the blow off valve 213 that opens and closes on the switching interlock ground with air suction valve 211 is driven valve, via exhausr port 214 guiding freeing pipes 215.
On the other hand, upstream side in aspirate tube 207, air suctiton inlet 210 is equipped with the throttle gate 208 to regulating with the relevant aspirated air amount of aspirated air that imports through not shown fil.This throttle gate 208 constitutes, by the throttle motor that is electrically connected with ECU100 209 its driving conditions of control.In addition; ECU100 basically with obtain with the aperture of not shown acceleration pedal (promptly; Above-mentioned accelerator open degree Ta) mode of cooresponding throttle opening is controlled throttle motor 209, but also can via the meaning ground of actuator throttle opening not adjusted via the action control of throttle motor 209.That is, throttle gate 208 constitutes as a kind of electronic control type throttle gate.
Three-way catalyst 216 is set on freeing pipe 215.Three-way catalyst 216 constitutes and can purify CO (carbonic oxide), HC (carbohydrate) and the NOx (oxides of nitrogen) that discharges from driving engine 200 respectively.In addition; The mode of taking of catalyst-assembly involved in the present invention is not limited to such three-way catalyst, for example can replace three-way catalyst or the NSR catalyst (NOx occlusion reducing catalyst) or the various catalyst of OC/OCAT are set except that three-way catalyst.
At freeing pipe 215, be provided with and constitute the air-fuel ratio sensor 217 that can detect the exhaust air-fuel ratio of driving engine 200.And then, at the water jacket that is arranged at the cylinder body of taking in cylinder 201, be equipped with supplying with the cooling-water temperature sensor 218 that the relevant coolant water temperature of cooling water expansion tank (LLC) be used for cooled engine 200 detects with circulation.These air-fuel ratio sensors 217 and cooling-water temperature sensor 218 are electrically connected with ECU100 respectively, constitute the air/fuel ratio and the coolant water temperature that are detected and are grasped by constant or inconstant sense cycle by ECU100 respectively.
Return Fig. 2, dynamotor MG1 is that an example of " rotating machine " involved in the present invention is a dynamotor, constitutes to have electric energy is changed into the power operation effect of kinetic energy and kinetic energy changed into the actification of electric energy.Dynamotor MG2 is the big dynamotor of volume ratio dynamotor MG1, and MG1 is same with dynamotor, constitutes to have electric energy is changed into the power operation effect of kinetic energy and kinetic energy changed into the actification of electric energy.In addition; Dynamotor MG1 and MG2 for example constitute as motor-alternator; For example both can have and possess the structure that has rotor with the stator of the three-phase coil of the formation rotating field of reeling of a plurality of permanent magnets at outer peripheral face, also can have other formations.
Power division mechanism 300 is that an example of " Poewr transmission mechanism " involved in the present invention is a distributing means for power supply, and it example that possesses " first rotating element " involved in the present invention that be arranged on central part is sun gear S1, be the example of " second rotating element " involved in the present invention that concentric circles is arranged on the periphery of sun gear S1 is gear ring R1, be configured between sun gear S1 and the gear ring R1 and a plurality of miniature gears P1 of in the periphery rotation of sun gear S1, revolving round the sun, a example that the S. A. of these miniature gearss is carried out " the 3rd rotating element " involved in the present invention of axle supporting are pinion carrier C1.
At this, sun gear S1 is connected with the rotor of MG1 via sun gear shaft 310, and the rotative speed of its rotative speed and MG1 is that MG1 rotative speed Ng is of equal value.In addition, gear ring R1 combines with the not shown rotor of MG2 via axle drive shaft 600 and speed reduction gearing 700, and the rotative speed of its rotative speed and MG2 is that MG2 rotative speed Nm is of equal value.And then the input shaft 500 on the bent axle 205 of pinion carrier C1 and the explanation formerly that is connected driving engine 200 is connected the combustion engine rotative speed NE of its rotative speed and driving engine 200 equivalence.In addition, in hybrid drive 10, MG1 rotative speed Ng and MG2 rotative speed Nm are detected by the constant cycle by rotation sensors such as resolvers respectively, flow to ECU100 by the constant or inconstant cycle.
On the other hand; Axle drive shaft 600 comprises the speed reduction gearing 700 of the speed reduction gearing of various reducing gear via conducts such as difies; With drive wheel to motor vehicle driven by mixed power 1 be that axle drive shaft SFR and the SFL (that is, these axle drive shafts are examples of " axletree " involved in the present invention) that off front wheel FR and the near front wheel FL drive respectively connects.Therefore; Supply to the motor torque Tm of axle drive shaft 600 from dynamotor MG2; Transmit to each axle drive shaft via speed reduction gearing 700, the propulsive effort from each drive wheel via each axle drive shaft transmits is input to dynamotor MG2 via speed reduction gearing 700 and axle drive shaft 600 equally.That is, the speed V of MG2 rotative speed Nm and motor vehicle driven by mixed power 1 has unique corresponding relationship.
In this constitutes; Power division mechanism 300 will be supplied to the motor torque Te of input shaft 500 from driving engine 200 via bent axle 205 by pinion carrier C1 and miniature gears P1; The as prescribed ratio (with the mutual gear of each gear than cooresponding ratio) be assigned to sun gear S1 and gear ring R1, can the power of driving engine 200 be divided into two systems.
In order to understand the action of power division mechanism 300 easily; To defining than ρ as the number of teeth of sun gear S1 gear with respect to the number of teeth of gear ring R1; Then under the situation of 200 couples of pinion carrier C1 of driving engine effect motor torque Te; The torque Tes that is revealed in sun gear shaft 310 is expressed by following (1) formula, and the torque Ter that is revealed in axle drive shaft 600 is in addition expressed by following (2) formula.
Tes＝-Te×ρ/(1+ρ)(1)
Ter＝Te×1/(1+ρ)(2)
In addition, the structure of the embodiment that " Poewr transmission mechanism " involved in the present invention is related is not limited to the form of power division mechanism 300.For example; Poewr transmission mechanism involved in the present invention also can possess a plurality of sun and planet gears; The a plurality of rotating elements that sun and planet gear possessed suitably are connected with a plurality of rotating elements that other sun and planet gears are possessed separately, constitute the modified roll mechanism of one.In addition; The related speed reduction gearing 700 of this embodiment only slows down according to the rotative speed of predefined reduction ratio to axle drive shaft 600; But motor vehicle driven by mixed power 1 also can with this speed reduction gearing dividually, possess and for example have a plurality of clutch mechanisms or stop mechanism step change device as a plurality of speed change levels of composed component.It for example also can be such structure; That is, between dynamotor MG2 and speed reduction gearing 700, folder is established the sun and planet gear equal with power division mechanism 300; The rotor that on the sun gear of this sun and planet gear, connects MG2; On gear ring, connect gear ring R1, and pinion carrier is fixed with the mode that can not rotate, thereby the rotative speed Nm of MG2 is slowed down.
Stop mechanism 400 is to have that a slipper is connected with sun gear S1 and another slipper is known hydraulic-driven wet multi-plate type brake equipment with fixing example structure, " lockout mechanism " involved in the present invention of physics mode.Stop mechanism 400 is connected with not shown fluid pressure drive device; Be pressed on the slipper of fixation side through the hydraulic pressure supplied with from this fluid pressure drive device slipper the sun gear side, constitute can be selectively between the lock-out state that can not rotate and the unlock state that can rotate the state of main dispatching centre gear S1.In addition, the fluid pressure drive device of stop mechanism 400 is electrically connected with ECU100, constitutes by ECU100 and controls its action upperly.
In addition; Stop mechanism 400 is examples of the adoptable practice mode of " lockout mechanism " involved in the present invention; Lockout mechanism involved in the present invention for example also can adopt electromagnetism dental clutch mechanism or electromagnetism cam lock mechanism etc. except the stop mechanism 400 as wet multi-plate type brake equipment as a suitable mode.
< action of embodiment >
< locking the selection of the speed change pattern that carries out by MG1 >
The related motor vehicle driven by mixed power 1 of this embodiment can be according to the state of sun gear S1, selects fixedly speed change pattern or stepless shift mode as speed change pattern involved in the present invention.At this, the speed change pattern of motor vehicle driven by mixed power 1 is described with reference to Fig. 4.At this, Fig. 4 is the action alignment chart of hybrid drive 10.In addition, in the figure, the position with Fig. 2 repetition is marked identical Reference numeral and suitably omits its explanation.
In Fig. 4 (a), the longitudinal axis is represented rotative speed, and transverse axis is represented dynamotor MG1 (unique corresponding sun gear S1), driving engine 200 (unique corresponding pinion carrier C1) and dynamotor MG2 (unique corresponding gear ring R1) successively from a left side.At this; Power division mechanism 300 is the binary sun and planet gears of rotation; Constitute under the situation that the rotative speed of two elements among sun gear S1, pinion carrier C1 and the gear ring R1 is confirmed, the rotative speed of a remaining rotating element must be confirmed.That is, on the action alignment chart, the operating state of each rotating element can be by representing with the cooresponding one to one action conllinear of an operating state of hybrid drive 10.In addition, at the point of suitably representing after this on action alignment chart by operating point mi (i is a natural number).That is, an operating point mi is corresponding with a rotative speed.
In Fig. 4 (a), the operating point of establishing MG2 is operating point m1.In this case, if the operating point of MG1 is operating point m3, be that the operating point of pinion carrier C1 bonded assembly driving engine 200 becomes operating point m2 then with a remaining rotating element.At this moment, if under the state of the rotative speed of keeping axle drive shaft 600, make the operating point of MG1 be varied to operating point m4 and operating point m5, then the operating point of driving engine 200 is varied to operating point m6 and operating point m7 respectively.
That is, in this case,, can make driving engine 200 actions by desirable operating point through dynamotor MG1 is made as rotation speed control device.With the cooresponding speed change pattern of this state be stepless shift mode.In stepless shift mode, the operating point of driving engine 200 (operating point under said this situation is by the combination regulation of combustion engine rotative speed and motor torque Te), control becomes the minimum best burnup operating point of specific consumption of fuel of driving engine 200 basically.In addition, certainly in stepless shift mode, it is variable needing MG1 rotative speed Ng.For this reason, under the situation of selecting stepless shift mode, stop mechanism 400 is controlled its driving condition with the mode that sun gear S1 becomes release position.
Carry out supplemental instruction at this; In power division mechanism 300; For axle drive shaft 600 is supplied with and the cooresponding torque Ter of motor torque Te that explains before; Need will with the reaction force torque of aforesaid torque Tes equal and opposite in direction that in sun gear shaft 310, shows and sign-inverted (promptly negative torque) corresponding to motor torque Te, supply to sun gear shaft 310 from dynamotor MG1.In this case, at operating point m3 or the such operating point place that just changes the zone of operating point m4, MG1 becomes the generating state that just changes negative torque.Promptly; In stepless shift mode; Through dynamotor MG1 (unique corresponding sun gear S1) is played a role as the antagonistic force element,, and generate electricity by the part of the motor torque Te that distributes to sun gear shaft 310 to the part of axle drive shaft 600 supply engine torque Te.Not enough in the through torque of driving engine under the situation of axle drive shaft 600 desired torques, to utilize the form of this generation power, axle drive shaft 600 is suitably supplied with torque Tm from dynamotor MG2.
On the other hand, for example when the high speed light load is gone etc., for example under the low operating condition that gets final product and so on of MG2 rotative speed Nm height and combustion engine rotative speed NE, MG1 becomes the for example such negative operating point that changes the zone of operating point m5.In this case, dynamotor MG1 is as the negative torque of the reaction force torque of motor torque Te output, become negatively change, the state of negative torque and become the power running state.That is, in this case, come the torque Tg of automotor-generator MG1 can pass to axle drive shaft 600 as the driving torque of motor vehicle driven by mixed power 1.
On the other hand, dynamotor MG2 requires the torque excessive torque for what absorb with respect to outputed to axle drive shaft 600, becomes negative torque conditions.In this case, dynamotor MG2 just becomes and changes, the state of negative torque, becomes generating state.Under this state, produced the generating that will be used in from the propulsive effort of MG1 among the MG2, MG1 carried out the electrical path that the power operation drives the low efficiency of so so-called power cycle by this generation power.Under the state that has produced power cycle, the transmission efficiency of hybrid drive 10 reduces, and the system effectiveness of hybrid drive 10 reduces.
So, in motor vehicle driven by mixed power 1, in the operation range of confirming as the mode that can produce such power cycle in advance, the lock-out state of explanation before stop mechanism 400 is controlled so as to.Its kind attitude is shown in Fig. 4 (b).When stop mechanism 400 becomes lock-out state, that is, when center gear S1 was locked, dynamotor MG1 also must become lock-out state, and it is zero operating point m8 that the operating point of MG1 becomes rotative speed.Thereby the operating point of driving engine 200 becomes operating point m9, and its combustion engine rotative speed NE is by confirming (that is, converter speed ratio is certain) accordingly with the unique cooresponding MG2 rotative speed Nm of speed V is unique.The cooresponding speed change pattern of situation that is in the lock state with MG1 like this is fixing speed change pattern.
In fixing speed change pattern, former should can the replacement by the physics braking force of stop mechanism 400 by the reaction force torque of the motor torque Te of dynamotor MG1 burden.That is, under generating state and power running state, all need not to control dynamotor MG1, dynamotor MG1 is stopped.Therefore, need not dynamotor MG2 running basically, MG2 can be described as idling conditions.The result; In fixing speed change pattern; The driving torque that is revealed in axle drive shaft 600 only is to be divided into the through composition (with reference to above-mentioned (2) formula) of axle drive shaft 600 sides by power division mechanism 300 among the motor torque Te; Hybrid drive 10 only carries out the mechanical power transmission, and its transmission efficiency is improved.
< drag torque detects the particular case of control >
Stop mechanism 400, in the former situation that should be in release position, sometimes slipper each other the engaging power of effect fail complete cancellation and produce drag torque.Drag torque is a kind of loss torque that originally was not susceptible to its generation, can be described as the functional fault in the motor vehicle driven by mixed power 1, is being important so it detects aspect making that motor vehicle driven by mixed power 1 works efficiently.So, in motor vehicle driven by mixed power 1, carry out drag torque by ECU100 and detect control, can detect drag torque reliably.
At this, the particular case that drag torque detects control is described with reference to Fig. 5.At this, Fig. 5 is the diagram of circuit that drag torque detects control.
In Fig. 5, ECU100 judges the detection of drag torque regularly whether arrive (step S101).The detection of said drag torque regularly; The various drag torques that are suitable for that are meant following explanation detect the timing of handling; And, in order to prevent to carry out the detection of drag torque, be configured to appropriateness and suppress it and carry out frequency with the high-frequency of degree of infringement significance.
ECU100; At current time be not under the timer-operated situation of detection of drag torque (step S101: not), execution in step S101 repeatedly, on the other hand; Under the situation that the detection of drag torque regularly arrives (step S101: be), carry out drag torque and detect and handle (step S102).
At this, the related various drag torques of step S102 are detected processing describe.
< first method of inspection >
At first, with reference to Fig. 6 drag torque being detected the first related method of inspection describes.At this, Fig. 6 is the action alignment chart of hybrid drive 10.In addition, in the figure, mark identical Reference numeral and suitably omit its explanation for position with Fig. 4 repetition.In addition, in Fig. 6, Fig. 6 (a) expression MG1 is in the situation of just changeing state, and Fig. 6 (b) expression MG1 is in the situation of negative commentaries on classics state.
At this; In stepless shift mode; Under the situation of driving engine 200 output motor torque Te, the torque that should supply with from dynamotor MG1 as rotation speed control device be MG1 torque Tg be with the cooresponding negative torque of torque of calculating by above-mentioned (1) formula be reaction force torque.
In Fig. 6 (a), motor torque Te is Te=Te0.In this case, the MG1 torque Tg that does not produce under the normal condition of drag torque Tgloss at stop mechanism 400 is diagram Tg0base.
On the other hand, stop mechanism 400 is to be used for mechanism that dynamotor MG1 is locked, acts on slipper drag torque Tgloss each other and always acts on the direction that dynamotor MG1 is stopped.That is, be under the situation of just changeing state at MG1 as Fig. 6 (a), the action direction of drag torque Tgloss and reaction force torque are that the direction of MG1 torque Tg is consistent.
Therefore, in this case, drag torque Tgloss plays a role as the part of reaction force torque, and following (3) formula is set up.That is, the MG1 torque Tg0 of the reality that should supply with from dynamotor MG1 for the reaction force torque of bearing motor torque Te0, its absolute value than before the amount of little this drag torque of Tg0base Tgloss.In addition, because reaction force torque is negative torque, so in this case, as if the magnitude relationship by the torque that comprises positive and negative Reference numeral, it is big that the MG1 torque becomes.Like this, producing under the situation of drag torque Tgloss at stop mechanism 400 under the just commentaries on classics state of MG1, the output torque of dynamotor MG1 is MG1 torque Tg, compares with the situation that does not produce drag torque Tgloss to become big.
Tg0＝Tg0base-Tgloss(3)
ECU100 utilizes the generation of this relationship detection drag torque Tgloss.Promptly; ECU100 according to the actual drive condition of dynamotor MG1 (for example; Drive current or its controlling quantity supplied with via PCU11 are dutycycle) etc.; Calculate the torque (that is, with the cooresponding torque of above-mentioned Tg0, an example of " first torque " involved in the present invention) of dynamotor MG1 real output.On the other hand, the torque of the script under the situation that does not produce drag torque Tgloss (that is, with the cooresponding torque of above-mentioned Tg0base) can be calculated according to the operating condition of motor vehicle driven by mixed power 1.Promptly; Except the operating condition of transition; If known with based on by accelerator open degree sensor 13 detected accelerator open degree Ta and by the determined corresponding driving engine requirement of propulsive effort output Pne and the combustion engine rotative speed Ne of requiring of car speed sensor 14 detected speed V, then can utilize these parameters to calculate motor torque Te.If calculate motor torque Te, then can be according to above-mentioned (1) formula based on the gear ratio of power division mechanism 300, obtain the value of the former MG1 torque (that is an example of " second torque " involved in the present invention) that should supply with from MG1.
Under the normal condition that does not produce drag torque Tgloss, MG1 torque Tg0 and Tg0base should equate, if MG1 torque Tg0 (first torque), then can draw the judgement that produces drag torque Tgloss than Tg0base (second torque) big (little as absolute value).In addition, this judgement is an example of the action of " judging unit " involved in the present invention, but this moment, and ECU100 also can surpass the generation of considering error or various situation in advance and detecting drag torque Tgloss during preset threshold in both residual quantity.
On the other hand, in Fig. 6 (b), motor torque Te is Te=Te1.In this case, the MG1 torque Tg that does not produce under the normal condition of drag torque Tgloss at stop mechanism 400 is diagram Tg1base.
At this; As aforementioned; Drag torque Tgloss owing to always act on makes on the direction that dynamotor MG1 stops, so be under the situation of bearing the commentaries on classics state at MG1 as Fig. 6 (b), the action direction of drag torque Tgloss and reaction force torque are the in the opposite direction of MG1 torque Tg.
Therefore, in this case, drag torque Tgloss is towards the directive effect of the effect that hinders reaction force torque, and following (4) formula is set up.That is, be used to bear the MG1 torque Tg1 of the reality that should supply with from dynamotor MG1 of the reaction force torque of motor torque Te1, absolute value is than the amount of formerly big this drag torque Tgloss of Tg1base.In addition, because reaction force torque is negative torque, so in this case, if with the magnitude relationship of the torque that comprises positive and negative Reference numeral, then the MG1 torque diminishes.Like this, producing under the situation of drag torque Tgloss at stop mechanism 400 under the negative commentaries on classics state of MG1, the output torque of dynamotor MG1 is MG1 torque Tg, compares with the situation that does not produce drag torque Tgloss to diminish.
Tg1＝Tg1base-Tgloss (4)
Under the normal condition that does not produce drag torque Tgloss; MG1 torque Tg0 and Tg0base should equate; Be at MG1 under the situation in negative commentaries on classics zone; If MG1 torque Tg0 (first torque), then can draw the judgement that produces drag torque Tgloss than Tg0base (second torque) little (big as absolute value).
At this, the change of particularly such MG1 torque Tg may not be only because of drag torque Tgloss produces, and also can produce because of the deviation of the output characteristic of driving engine 200.That is, under the situation of Fig. 6 (a), should be Te0 originally with motor torque Te and have nothing to do, if, then also correspondingly change from the MG1 torque Tg that dynamotor MG1 supplies with from driving engine 200 output motor torque Te0 '.
Yet; The influence that the deviation of such engine output characteristics is brought to reaction force torque; Can do not changed by the rotary area of dynamotor MG1, if motor torque Te moves to increasing lateral deviation, then its absolute value of reaction force torque becomes big; If move to reducing lateral deviation, then its absolute value of reaction force torque diminishes.Therefore; Be at dynamotor MG1 under situation of just changeing state and the situation that is in negative commentaries on classics state; If carry out above-mentioned comparison process respectively, the skew that then can distinguish MG1 torque Tg still is because drag torque Tgloss causes owing to driving engine 200 sides cause.That is, can detect the generation of drag torque Tgloss exactly.
< second method of inspection >
Then, with reference to Fig. 7 the second related method of the detection of drag torque Tgloss is described.At this, Fig. 7 is that illustration utilizes the MG1 of stop mechanism 400 to lock the schematic time response figure of the time lapse of timer-operated MG1 rotative speed Ng.
In Fig. 7; At the moment T0 MG1 locking indication appears (promptly; With speed V and require situation etc. that propulsive effort Ft meets predefined MG1 ' locked ' zone quite); Dynamotor MG1, begins its rotative speed is controlled in order to make MG1 rotative speed Ng to zero rotating speed convergence from the state of MG1 rotative speed Ng=A.
At this, in lockout mechanism 400, do not produce under the situation of drag torque Tgloss, as diagram solid line institute was illustrative, MG1 rotative speed Ng converged on zero rotating speed at moment T2.On the other hand; In lockout mechanism 400, produce under the situation of drag torque Tgloss, that kind as described before is because drag torque Tgloss is always to the directive effect of the rotation that stops MG1; So, compare normal circumstances to convergence rate that kind shown in the diagram dotted line of zero rotating speed and shift to an earlier date to some extent.Its result, MG1 converges on zero rotating speed at the moment T1 that shifts to an earlier date than normal circumstances.
ECU100 (, an example of described before " detecting regularly ") when carrying out the MG1 locking measures the convergence rate of MG1 rotative speed Ng.At this moment; If grasp the convergence property of the Ng under the normal circumstances or locking the mensuration of carrying out the convergence rate of Ng when indicating whenever sending MG1 during the action of motor vehicle driven by mixed power 1 through experiment in advance; Then converge under the situation of zero rotating speed than the convergence time under the normal circumstances in advance or comparing with other example values under the situation that obviously converges on zero rotating speed in advance, can draw and produce the such judgement of drag torque Tgloss at MG1 rotative speed Ng.
< the 3rd method of inspection >
Then, with reference to Fig. 8 the related third party's method of the detection of drag torque Tgloss is described.At this, the time response figure of the time lapse of reaction force torque Tg and the combustion engine rotative speed Ne of Fig. 8 when to be that illustration is stable go.In addition, in the figure, suitably omit its explanation to representing with the position identical accompanying drawing of mark that Fig. 7 repeats.
In Fig. 8; Reaching stable going (in addition; Said " stable go " is meant: remove be attended by acceleration and deceleration or be attended by motoring condition outside the operating condition of over load change, more stable) during moment T0, ECU100 reduces reaction force torque.In addition, because reaction force torque is negative torque, so " reducing " is the meaning that the top of MG1 torque Tg in figure changed.
Under the situation that reaction force torque is reduced; Stablizing the equilibrium that motor torque Te and reaction force torque under the motoring condition be MG1 torque Tg is destroyed; The absolute value of motor torque Te surpasses the absolute value of reaction force torque, and the combustion engine rotative speed Ne of driving engine 200 rises.Yet the ascending amount of combustion engine rotative speed Ne of this moment has produced in stop mechanism 400 under the situation of drag torque Tgloss and be different under the situation that does not produce drag torque Tgloss.
That is, drag torque Tgloss is owing to always act on the direction that stops dynamotor MG1 rotation, and MG1 is connected via power division mechanism 300 with driving engine 200, so, on combustion engine rotative speed Ne, also occur being somebody's turn to do influencing.In Fig. 8, the characteristic that does not produce the combustion engine rotative speed Ne under the normal circumstances of drag torque Tgloss representes with solid line, and the characteristic that has produced the combustion engine rotative speed Ne under the situation of drag torque Tgloss in addition is represented by dotted lines.Like this, under situation about under the situation that has produced drag torque Tgloss and not producing, separately and the counter-rotating of the magnitude relationship between the threshold value B.Thereby, for example, then can detect drag torque Tgloss exactly if suitably confirm the value (needn't compare) of threshold value B in advance through experiment with threshold value.
At this, Fig. 8 is that dynamotor MG1 is in the movement under the situation of just changeing state, is under the situation of negative commentaries on classics state the counter-rotating of the relation of solid line and dotted line at MG1.Promptly; When in negative commentaries on classics zone, removing reaction force torque, the direction that drag torque Tgloss acted on is consistent with the direction that the rotation that promotes driving engine 200 is risen, so; Compare with the situation that does not produce drag torque Tgloss, combustion engine rotative speed Ne rises all the better significantly.; In any case under the situation that produces drag torque Tgloss with the situation that does not produce drag torque Tgloss under the movement of combustion engine rotative speed Ne when removing reaction force torque change and all do not have variation on different these aspects, do not consider that the hand of rotation of MG1 just can carry out the detection of drag torque Tgloss.
< the 4th method of inspection >
Then, with reference to Fig. 9 the related cubic method of the detection of drag torque Tgloss is described.At this, the time response figure of the starting torque Tclk when Fig. 9 is the illustration engine starting, combustion engine rotative speed Ne and a combustion engine rotative speed variation delta Ne time lapse separately.In addition, in the figure, the position with Fig. 8 repetition is marked identical Reference numeral and suitably omits its explanation.
In Fig. 9, MG1 torque Tg is the starting torque that is used for driving engine 200 startings.Output characteristic as the MG1 torque under the situation of starting torque effect is confirmed through experiment in advance, in Fig. 9, representes with solid line.
Make under the situation of starting torque to driving engine 200 effects with predetermined like this characteristic, according in stop mechanism 400, whether producing drag torque Tgloss, the rising characteristic of combustion engine rotative speed Ne is different.Promptly; For example under the situation that does not produce drag torque Tgloss; If combustion engine rotative speed Ne sets up by the time response shown in the diagram solid line, and under the situation that produces drag torque Tgloss, combustion engine rotative speed Ne sets up by the time response shown in the diagram dotted line.Its result, combustion engine rotative speed variation delta Ne also become the relation shown in diagram solid line and the dotted line, separately and the magnitude relationship between the threshold value C reverse each other.Thereby for example if suitably confirm the value (needn't compare with threshold value) of threshold value C in advance through experiment, ECU100 can detect drag torque Tgloss exactly when making driving engine 200 startings.
At this, Fig. 9 is that dynamotor MG1 is in the movement under the situation of just changeing state, that is, the engine starting that begins with the state that stops from motor vehicle driven by mixed power 1 is corresponding.On the other hand, when motor vehicle driven by mixed power 1 utilizes the motor torque Tm that supplies with from dynamotor MG2 to be in the EV motoring condition etc. under the situation, driving engine 200 is in the state of Ne=0 according to the size of its friction, and when engine starting, MG1 becomes negative commentaries on classics state.
In this case, the relation of solid line and dotted line counter-rotating.That is, be in the engine starting under the situation of negative commentaries on classics state for MG1, the drag torque Tgloss on the direction of the action direction of starting torque and the rotation that acts on prevention MG1 is consistent.Therefore, become the form that the rising of MG1 rotative speed Ng obtains promoting, the rising that becomes combustion engine rotative speed Ne simultaneously also obtains the form that promotes.In a word; Under the situation that produces drag torque Tgloss and do not produce under the situation of drag torque Tgloss; Changing with respect to the movement of the starting torque of giving by identical characteristics at combustion engine rotative speed Ne does not all have on the different this point to change, and can not carry out the detection of drag torque Tgloss even do not consider the hand of rotation of MG1 yet.
Be back to Fig. 5, when detecting processing through the various drag torques of carrying out according to above-mentioned various method of inspections, ECU100 judges whether to produce drag torque (step S103).If (step S103: not), then ECU100 makes MIL (the Multi Information Lump: multi-functional display lamp) turn off the light (step S105), processing is turned back to step S101 of the car chamber interior that is arranged on motor vehicle driven by mixed power 1 not produce drag torque.
On the other hand; Under the situation of the generation that detects drag torque (step S103: be); ECU100 calculates the normal circumstances out-of-position side-play amount (step S104) of the various desired values (for example, convergence rate of the variable quantity of combustion engine rotative speed Ne or MG1 rotative speed Ng etc.) that are used to judge whether to produce drag torque in this drag torque and the above-mentioned various method of inspection.This side-play amount is calculated as the part that this detection is handled when execution is handled according to the detection of above-mentioned various method of inspections.
When calculating side-play amount, ECU100 judges whether this side-play amount is (step S106) below the specified value.Said this specified value is through testing definite appropriate value.(step S106: not), ECU100 makes the bright lamp of MIL (step S109), and processing is turned back to step S101 under the side-play amount situation bigger than specified value.
On the other hand; In side-play amount is (step S106: be) under the situation below the specified value; Substitute and make the bright lamp of MIL, ECU100 revises (step S107) through making the starting torque Tgclk that when driving engine 200 starts, supplies with from dynamotor MG1 move predefined correction amount alpha with respect to a reference value Tgclkbs to the increase lateral deviation.The related correction amount alpha of the correction of this starting torque is configured to: in the process of driving engine 200 starting, combustion engine rotative speed Ne with the degree that can not cause Vehicular vibration in advance through driving engine 200 near intrinsic resonance bands (for example the 400rpm).
In addition; ECU100; When driving engine 200 stops, from dynamotor MG1 supply the torque of reduction Tgbrk is arranged, make reduction torque Tgbrk move predefined correction β to reducing lateral deviation, revise (step S108) thus with respect to a reference value Tgbrkbs for driving engine 200 is stopped.The related correction β of the correction of this starting torque is configured to: in the process that driving engine 200 is stopped, combustion engine rotative speed Ne with the degree that can not cause Vehicular vibration in advance through driving engine 200 near intrinsic resonance bands (for example the 400rpm).When execution in step S108, handle turning back to step S101.
Like this, the drag torque related according to this embodiment detects control, handles through the various detections according to above-mentioned various method of inspections, can detect the drag torque that in stop mechanism 400, produces in advance.Therefore; Can adopt to make the bright lamp of MIL come to suppress the various countermeasures such as vibration generation that cause because of resonance, can guarantee the reliability of motor vehicle driven by mixed power 1 to the functional fault of Pilot Report's stop mechanism 400 or through starting torque or the correction that reduces torque.In addition; Various detections according to above-mentioned various method of inspections are handled; Because carried out neatly under the various conditions when comprising stable going, during the MG1 locking or during starting etc., thus fully guaranteed the detection frequency of drag torque, thereby in practice, be useful.
< second embodiment >
In above-mentioned first embodiment, use be the structure that when hybrid drive 10 adopts fixing speed change pattern, locks MG1.The structure of the hybrid drive when, obtaining fixing speed change pattern is not limited to such MG1 and locks.At this, the structure of other hybrid drive is described with reference to Figure 10.At this, Figure 10 is the summary pie graph that the structure of the hybrid drive 20 that second embodiment of the present invention is related represented in summary.In addition, in the figure, the position with Fig. 2 repetition is marked identical Reference numeral and suitably omits its explanation.
In Figure 10, hybrid drive 20 possesses on power division mechanism 800 these aspects in alternate power division mechanism 300 another example as " Poewr transmission mechanism " involved in the present invention, constitutes different with hybrid drive 10.Power division mechanism 800 is as the modified roll mechanism that is made up of a plurality of rotating elements, adopts the mode of so-called cured civilian Nao formula sun and planet gear of second sun and planet gear 820 of first sun and planet gear 810 that possesses single pinion type and double-pinion type.
First sun and planet gear 810 possesses sun gear 811, pinion carrier 812, gear ring 813 and miniature gears 814, wherein, miniature gears 814 with rotation on the axis direction and through pinion carrier 812 certainly then the revolution mode remain on the pinion carrier 812; And with 813 engagements of sun gear 811 and gear ring; And first sun and planet gear 810 constitutes, and sun gear 811 is connected with the rotor of dynamotor MG1; Pinion carrier 812 is connected with input shaft 500, and gear ring 813 is connected with axle drive shaft 600.
Second sun and planet gear 820 possess sun gear 821, pinion carrier 822, gear ring 823 and with sun gear 821 ingear miniature gearss 825 and with gear ring 823 ingear miniature gearss 824; Wherein, Miniature gears 825 and miniature gears 824 with rotation on the axis direction and through pinion carrier 822 certainly then the revolution mode remain in respectively on the pinion carrier 822; And second sun and planet gear 820 constitutes, and sun gear 821 is connected with a slipper of stop mechanism 400.That is, in this embodiment, sun gear 821 as " first rotating element " involved in the present invention another example and play a role.
Like this; Power division mechanism 800 possesses as a whole: the sun gear 821 (first rotating element) of the sun gear 811 of first sun and planet gear 810, second sun and planet gear 820, the first rotating element group that is made up of the gear ring 823 of the pinion carrier 812 of interconnective first sun and planet gear 810 and second sun and planet gear 820, the second rotating element group that also has the pinion carrier 822 by the gear ring 813 of interconnective first sun and planet gear 810 and second sun and planet gear 820 to constitute amount to four rotating elements.
According to hybrid drive 20; When center gear 821 becomes lock-out state, its rotative speed and is zero; By having and the second rotating element group of the unique cooresponding rotative speed of speed V and this sun gear 821, limit the i.e. rotative speed of the first rotating element group of a remaining rotating element.The pinion carrier 812 that constitutes the first rotating element group is owing to be connected with the input shaft 500 of the bent axle 205 that is connected in driving engine 200 (not shown); So consequently; The combustion engine rotative speed NE of driving engine 200 becomes and the unique corresponding relationship of speed V, has realized fixedly speed change pattern.Like this, fixedly speed change pattern also can be achieved in the structure beyond the hybrid drive 10, and with it correspondingly, the lock object of stop mechanism 400 also can suitably change.In a word, as long as have the stop mechanism 400 that can produce drag torque, the method for inspection with the illustrative drag torque involved in the present invention of various forms all is an actv. in the first embodiment.
< the 3rd embodiment >
Then, the 3rd embodiment of the present invention is described.
< structure of embodiment >
At first, with reference to Figure 11 the structure of the related hybrid drive 30 of the 3rd embodiment of the present invention is described.At this, Figure 11 is the summary pie graph of the summary structure of representing hybrid drive 30.In addition, in the figure, the position with Fig. 2 repetition is marked identical Reference numeral and suitably omits its explanation.
In addition, the related vehicle of the 3rd embodiment constitutes, and is except possessing hybrid drive 30, identical with above-mentioned motor vehicle driven by mixed power 1.In addition; In the 3rd embodiment; ECU100 constitutes can be according to the variable speed control of stating after the control program execution that is contained among the ROM, and an example separately that constitutes as " the 3rd control unit " involved in the present invention, " calculating the unit ", " amending unit " and " selected cell " plays a role.
In Figure 11, hybrid drive 30 possesses driving engine 200, power division mechanism 300, MG1, MG2, input shaft 500, axle drive shaft 600, speed reduction gearing 700 and lockout mechanism 900.
Lockout mechanism 900 is that an example of " lockout mechanism " involved in the present invention is a cam lock fixed pattern clamping close device; It comprises cam 910, clutch plate 920 and actuator 930 as the main composition element, constitute can be selectively between lock-out state that can not rotate and the release position that can rotate the state of main dispatching centre gear S1.That is, sun gear S1 is an example of " first rotating element " involved in the present invention.
At this, the concrete formation of lockout mechanism 900 is described with reference to Figure 12.At this, Figure 12 is the mode sectional drawing that a section of illustration lockout mechanism 900 constitutes.In addition, in the figure, the position with Figure 11 repetition is marked identical Reference numeral and suitably omits its explanation.
In Figure 12, lockout mechanism 900 possesses cam 910, clutch plate 920, actuator 930, retracing spring 940 and cam ball 950.
Cam 910, be connected with sun gear shaft 310, can be with the rotation of sun gear shaft 310 and sun gear S1 one, be a pair of roughly discoideus parts that engage with clutch plate 920.In addition, cam 910 needn't with sun gear shaft 310 direct connections, also can be connected indirectly with sun gear shaft 310 via various links.
Clutch plate 920 is to be constituted and disposed in opposite directions with cam 910, be a pair of discoideus parts that engage with cam 910 by the magnetic metal material.
Actuator 930 is to comprise attraction portion 931, electromagnet 932 and friction part 933 and the actuating device of formation.
Attraction portion 931 is the frameworks that constituted and constituted the actuator 930 that can take in electromagnet 932 by the magnetic metal material.It is on the casing CS that attraction portion 931 is fixed on the retaining element of roughly fixing integratedly with the outline parts of hybrid drive 30.
Electromagnet 932 is the magnet that constitutes under the excited state of the not shown drive division supply regulation power-transfer clutch engaging electric current I d (so-called exciting current) that supplies with from the electric power of battery 12 from reception, can produce magnetic force.Constitute; The magnetic force of under excited state, launching from electromagnet 932; Through the attraction portion 931 that constitutes by the magnetic metal material, attract aforesaid clutch plate 920 (that is, giving propulsive effort to clutch plate 920 towards the direction that clutch plate 920 is drawn to the electromagnet side draught is electromagnetic force).In addition, this drive division is electrically connected with ECU100, constitutes the excitation actuating of being controlled electromagnet 932 by ECU100 upperly.
Friction part 933 be formed in attraction portion 931 with clutch plate 920 face in opposite directions on the friction functive, compare with inchoate situation, set its friction coefficient so that can be in the moving of object of contact condition in wider prevention.
Retracing spring 940 is that a fixed end is fixed in clutch plate 920, another fixed end and can be fixed in the elastic body of the frame (not shown) of lockout mechanism 900 rotatably via bearing sub-assemblys such as bearings, to the direction application of force of clutch plate 920 to cam 910.Thereby clutch plate 920 receives the application force of this retracing spring 940 usually, stops to separate regulation interval GAP and attraction portion 931 non-contacting position in opposite directions in opposite directions.
Cam ball 950 is by the spherical power transmission member of cam 910 and clutch plate 920 clampings.Lockout mechanism 900 constitutes, and this cam ball 950 as transmitting element, will be passed to clutch plate 920 via the torque Tmg1 that sun gear S1 and sun gear shaft 310 pass to the dynamotor MG1 of cam 910.
At this, carry out bright more specifically to the structure of lockout mechanism 900 with reference to Figure 13.At this, Figure 13 is the schematic cross sectional view of in Figure 12, observing lockout mechanism 900 along arrow line A direction.In addition, in the figure, the position with Figure 12 repetition is marked identical Reference numeral and suitably omits its explanation.
In Figure 13; Cam 910 and clutch plate 920 forward surface separately; Form respectively more towards central part, the less thick to prolonging direction of sun gear shaft 310 separately, above-mentioned cam ball 950 is clamped near the maximum central part between the two space in opposite directions usually.Thereby, being at clutch plate 920 under the situation of above-mentioned non-contacting position, cam 910 and clutch plate 920 roughly are rotation integratedly with the transmitting element of this cam ball 950 as torque to the direction identical with the hand of rotation of dynamotor MG1.Therefore, be at clutch plate 920 under the situation of above-mentioned non-contacting position, the rotation of dynamotor MG1 does not at least substantially receive any obstruction.In addition, in Figure 13, the diagram below is defined as the positive veer of dynamotor MG1, and dynamotor MG1 not only can rotate to this positive veer, and can likewise be rotated to the clockwise sence just in time opposite with this positive veer (omitting diagram).
In addition, in this embodiment, MG2 and gear ring R1 are connected with same rotating element in the speed reduction gearing 700, and the rotative speed of MG2 rotative speed Nm and gear ring R1 is equal to, and MG2 and gear ring R1 also can be connected with different rotating element each other.In this case, the rotative speed of gear ring R1 and MG2 rotative speed Nm can have and the difference of regulation gear than cooresponding amount.Or, also can between MG2 and speed reduction gearing 700, clamp and possess the step change machine of gear than different each other a plurality of gear stage.
< action of embodiment >
< locking action of lockout mechanism 900 >
In hybrid drive 10, lockout mechanism 900 as first rotating element involved in the present invention, can switch the state of sun gear S1 sun gear S1 between lock-out state and release position selectively.In addition, sun gear S1 is connected with dynamotor MG1 as above-mentioned, and under the situation that sun gear S1 is in the lock state, MG1 also becomes the lock-out state that can not rotate.Therefore, the situation that sun gear S1 is in the lock state after this suitably shows as " MG1 is in the lock state " etc.At this, the locking action of the sun gear S1 that formed by lockout mechanism 900 is described with reference to Figure 14.At this, Figure 14 is explanation is transformed into the state of sun gear S1 the lock process of lock-out state from release position by the locking action of lockout mechanism 900 a schematic cross sectional view.In addition, in the figure, the position with Figure 12 or Figure 13 repetition is marked identical Reference numeral and suitably omits its explanation.
In Figure 14, Figure 14 (a) expression and before the same state of Figure 13 are pressed from both sides between clutch plate 920 and friction part 933 and are established space GAP in opposite directions, the influence of the restraint that clutch plate 920 does not receive to be formed by friction part 933 and can rotating.Thereby under the effect of cam ball 950, cam 910 can roughly be rotation integratedly with clutch plate 920.At this, cam 910 is connected with the rotor R T of MG1 via sun gear shaft 310, and this rotor R T is connected with sun gear S1 via sun gear shaft 310.Therefore, in hybrid drive 30, cam 910 can conduct moves with the rotating element of sun gear S1 one rotation.That is, under the state shown in Figure 14 (a), sun gear S1 also can not receive clutch plate 920 restriction be rotated.One example of this state and " unlock state " involved in the present invention quite.
In Figure 14 (b), the state of power-transfer clutch engaging electric current I d is supplied with in expression to the electromagnet 932 of actuator 930.That is, in this case, the electromagnetic force of launching from electromagnet 932 has influence on clutch plate 920 via attraction portion 931, and the application force of clutch plate 920 opposing retracing springs 940 moves to above-mentioned non-contacting position and is the contact position to the utmost point, is attracted portion's 931 absorption.Its result, space GAP subdues in opposite directions.In addition, become supply along with the electromagnetic force that is formed by excitation, friction part 933 form with respect to clutch plate 920 performance friction force, the Xiang Zhengzhuan of clutch plate 920 or the action of clockwise sence are hindered.That is, under this state, clutch plate 920 hinders its action by electromagnet 932 and friction part 933, with respect to actuator 930, promptly static with respect to casing CS.
On the other hand, so be attracted at clutch plate 920 under the state of portion's 931 absorption, substitute the GAP of space in opposite directions that subdues, between cam ball 950 and clutch plate 920, form groove GT along hand of rotation.Therefore, when cam 910 receive MG1 rotation influence and during to the rotation of positive veer or clockwise sence, only have cam 910 and cam ball 950 to move to its hand of rotation.In addition, at this, proceed explanation to the form that positive veer moves as them.At this, the new groove GT that kind as described before that forms is the inverted cone shape that section is watched, and along with cam ball 950 is advanced and tightened up gradually to hand of rotation, finally disappears and becomes groove and tighten up done state.Under groove tightened up done state, cam 910, cam ball 950 and clutch plate 920 were in contact with one another once more.
In Figure 14 (c), represent that such groove tightens up done state.Tightening up cam 910 under the done state at this groove will be under the situation of positive veer rotation, and the effect of the forward surface through being this back taper shape on cam ball 950, produces clutch plate 920 further to the thrust pressure of the direction pushing of actuator 930.Its result, cam 910 becomes lock-out state through this thrust pressure and the friction force that gives from friction part 933.Under this lock-out state, cam 910 is also same with clutch plate 920, becomes static with respect to casing CS, promptly fixing state.Its result, the sun gear S1 that rotates with cam 910 one also becomes the state fixing with respect to casing CS.Under lock-out state, the rotative speed of sun gear S1, promptly MG1 rotative speed Ng is zero.When the supply to the exciting current of electromagnet 932 stopped, under the effect of retracing spring 940, clutch plate 920 returned to original non-contacting position, and this lock-out state is disengaged.
< particular case of variable speed control >
At this, the particular case of the variable speed control carried out by ECU100 is described with reference to Figure 15.At this, Figure 15 is the diagram of circuit of variable speed control.
In Figure 15, ECU100 judges whether MG1 is in the lock state (step S201).(step S201: not), promptly under the situation of selecting stepless shift mode, ECU100 is execution in step S201 repeatedly under the situation that MG1 is not in the lock state.
On the other hand, under the situation that MG1 is in the lock state (step S201: be), ECU100 judges whether to satisfy the power-transfer clutch release conditions (step S202) of the locking of the MG1 should finish to be undertaken by above-mentioned lockout mechanism 900.That is, judge whether into from fixing speed change pattern to the switching timing of the speed change pattern of stepless shift mode.Under the situation that does not satisfy the power-transfer clutch release conditions (step S202), ECU100 returns processing to step S201, carries out a series of processing repeatedly.
When satisfying the power-transfer clutch release conditions (step S202: be), ECU100 carries out power-transfer clutch releasing and processing (step S203).Said power-transfer clutch releasing and processing, that kind promptly as described before is meant the supply to the drive current Id of electromagnet 932 that stops in the actuator 930.When stopping the supply of drive current Id, clutch plate 920 discharges from attraction portion 931 and friction part 933, and under the effect of retracing spring 940, clutch plate 920 returns to non-contacting position, and MG1 returns to the unlock state that can rotate.
When carrying out the power-transfer clutch releasing and processing, speed change pattern switches to stepless shift mode.When speed change pattern was switched to stepless shift mode, ECU100 calculated clutch friction load torque Tc (step S204).In addition, said clutch friction load torque Tc is an example of " drag torque " involved in the present invention, is owing to clutch plate 920 fails to discharge a kind of braking torque of supplying with from friction part 933 fully from friction part 933 because of some reason.
Before the calculation method of explanation clutch friction load torque Tc, the control flow of stepless shift mode is described with reference to Figure 16.At this, Figure 16 is the control block scheme of stepless shift mode.
In Figure 16, stepless shift mode is made up of control square frame B10 to B21.
At first, ECU100 obtains accelerator open degree Ta (control square frame B10), on this accelerator open degree Ta and then with reference to speed V, by require to drive try hard to confirm motor vehicle driven by mixed power 1 require propulsive effort Ft (control square frame B11).When confirming to require propulsive effort Ft, and then calculate driving engine requirement output Pn (control square frame B12).
When calculating driving engine requirement output Pn; Require output Pn to confirm that the target rotational speed of driving engine 200 is target engine rotative speed Netg (control square frame B13) based on this driving engine; According to the best burnup actuating wire of predesignating in the action point diagram, unique definite accordingly motor torque Te (control square frame B15).When definite motor torque Te,, calculate MG1 torque Tg (control square frame B16) according to based on above-mentioned (1) formula of the gear between the rotating element of power division mechanism 300 than regulation.
On the other hand, according to target engine rotative speed Netg, the expected value of confirming MG1 rotative speed Ng is target MG1 rotative speed Ngtg (control square frame B14).Target MG1 rotative speed Ngtg rotates the unique regulation accordingly of fast Netg by the rotative speed and the target engine that are in the axle drive shaft 600 of the unique corresponding relationship of speed V.When target MG1 rotative speed Ngtg confirms, obtain the MG1 rotative speed Ng (control square frame B18) of the current time that detects by testing agencies such as resolvers.
ECU100 calculates the deviation of target MG1 rotative speed Ngtg and MG1 rotative speed Ng, and the controlled reset amount of calculating the MG1 torque based on this deviation is MG1 torque value of feedback Tg (fb) (control square frame B16).For the MG1 torque value of feedback Tg (fb) that calculates,, this deviation is calculated (controlling square frame B19) as through torque Tep through the MG1 torque Tg and the deviation of this MG1 torque value of feedback Tg (fb) that in control square frame B16, calculates.
On the other hand, the ECU100 propulsive effort Ft torque that requires of calculating axle drive shaft as requested is that axle drive shaft requires torque Tn (control square frame B20), calculates the deviation of this axle drive shaft requirement torque Tn and through torque Tep.The deviation of calculating is as handling from the MG2 torque Tm that dynamotor MG2 supplies with.
At this; The said MG1 torque value of feedback Tg (fb) that in control square frame B17, calculates; Mainly be meant at the MG1 that MG1 rotative speed Ng is produced when zero rotating speed rises to target MG1 rotative speed Ngtg and the inertia torque of driving engine 200; But, also comprise this clutch friction load torque Tc under the situation of 700 pairs of MG1 effects of lockout mechanism clutch friction load torque Tc.Thereby poor as MG1 torque value of feedback Tg (fb) and this inertia torque can detect clutch friction load torque Tc.
Return Fig. 8, more specifically, ECU100 calculates clutch friction load torque Tc according to following (3) to (5) formula.In addition, in various, Te is a motor torque, and Tg is the MG1 torque, and Tg (fb) is the torque value of feedback, and Ig is the moment of inertia of MG1, and Ie is the moment of inertia of driving engine 200, and ρ is sun gear S1 and the gear ratio of gear ring R1, and ω is the cireular frequency of MG1.
Tdb＝ρ/(1+ρ)×Te-(Tg-Tg(fb))-(Ig+((ρ/(1+ρ))2×Ie)×dω/dt (3)
Tda＝ρ/(1+ρ)×Te-(Tg-Tg(fb))-(Ig+((ρ/(1+ρ))2×Ie)×dω/dt (4)
Tc＝Tda-Tdb (5)
At this, the formula of Tdb and Tda is equal to itself, calculates regularly different.That is, Tdb is the loss torque of the hybrid drive 10 before the power-transfer clutch engaging, and Tda is the loss torque of the hybrid drive 30 after power-transfer clutch discharges.In addition, after discharging with power-transfer clutch before the power-transfer clutch engaging, only be meant therebetween the state that is equal to across the engaging of power-transfer clutch.That is, above-mentioned (3) to (5) formula is whenever can both grasp the calculation processing how the loss torque changes across the engaging of a power-transfer clutch.Therefore, ECU100 constitutes, and the loss torque with a plurality of examples always is stored in RAM etc., and up-to-date loss torque is made as Tda, and the loss torque of calculating before the timing is made as Tdb, carries out above-mentioned (5) formula.
When calculating clutch friction load torque Tc, ECU100 judges that whether the clutch friction load torque Tc that is calculated is than threshold alpha big (step S205).If clutch friction load torque Tc is that (step S205: not), ECU100 as the drag torque of putting into practice the scope that goes up no problem, carries out common CVT pattern (stepless shift mode) (step S210), and processing is back to step S201 below the threshold alpha.
On the other hand; Under the clutch friction load torque Tc situation bigger (step S205: be) than threshold alpha; ECU100 judges that lockout mechanism 900 is in engaging fault (that is, an example of " faulty condition " involved in the present invention), advances the processing of handling when engaging fault.
Processing during as the engaging fault; At first; Fixedly between speed change pattern and the CVT pattern, carry out the comparison of the system effectiveness η sys of hybrid drive 10, judge the system effectiveness Elock system effectiveness Ecvt (step S206) in the not enough stepless shift mode whether in the fixing speed change pattern.If system effectiveness Elock is system effectiveness Ecvt above (step S206: deny); Promptly; When selecting fixing speed change pattern, can make under the situation that motor vehicle driven by mixed power 1 goes efficiently, and then whether judgement speed V when having selected fixedly speed change pattern is that driving engine stops (step S208) below the hump speed Vest.
Speed V ratio engine when having selected fixedly speed change pattern stops (step S208: deny) under the high situation of hump speed Vest, and ECU100 control lockout mechanism 900 locks MG1, and speed change pattern is changed to fixedly speed change pattern (step S211).On the other hand; Speed V when having selected fixedly speed change pattern is that driving engine stops (step S208: be) under the situation below the hump speed Vest; Perhaps under the system effectiveness Ecvt situation higher than system effectiveness Elock (step S206: be), ECU100 judges the temperature of lockout mechanism 900 is whether the temperature T mpc of power-transfer clutch portion is (step S207) below the higher limit Tmpcth.In addition, the said power-transfer clutch temperature T mpc of portion is the temperature of clutch plate 920, though not shown, in fact constitute by the temperature sensor that suitably is provided with on the position that is arranged on hybrid drive 30 and carry out suitable detection.In addition, this temperature sensor is electrically connected with ECU100, and the temperature T mpc of power-transfer clutch portion that is detected becomes the structure of carrying out reference by the constant or inconstant cycle by ECU100.
(step S207: not), ECU100 is controlled to the EV motor with hybrid drive 30, makes motor vehicle driven by mixed power 1 carry out EV and goes under the temperature T mpc of the power-transfer clutch portion situation higher than higher limit Tmpcth.That is, driving engine 200 and dynamotor MG1 stop its running.When beginning of going of being undertaken, handle being back to step S201 by the EV motor.
On the other hand, be (step S207: be) under the situation below the higher limit Tmpcth at the temperature T mpc of power-transfer clutch portion, ECU100 carries out power-transfer clutch fault CVT pattern (step S212).At this, the particular case of power-transfer clutch fault CVT pattern is described with reference to Figure 17.At this, Figure 17 is other block schemes of the stepless change control among the ECU100.In addition, in the figure, the position with Figure 16 repetition is marked identical Reference numeral and suitably omits its explanation.
In Figure 17, ECU100 constitutes, and with respect to the basic controlling square frame in the related stepless shift mode of Figure 16, has appended control square frame B22.In control square frame B22,, add clutch friction load torque Tc to getting deviation through deducting the MG1 torque value of feedback Tg (fb) that in control square frame B17, calculates from the MG1 torque Tg that among control square frame B16, calculates.That is, under the power-transfer clutch fault CVT pattern in Figure 15, the decrease of the through torque Tep of the driving engine that is caused by clutch friction load torque Tc is compensated.
More specifically describe; Handling according to basic controlling shown in Figure 16 under the situation of calculating the through torque Tep of driving engine; From MG1 torque Tg; Deduct the torque that has also added clutch friction load torque Tc except inertia torque, so the through torque Tep of the driving engine of calculating has reduced the amount of clutch friction load torque Tc.Its result deducts the MG2 torque Tm that the through torque Tep of driving engine calculates through require torque Tn from axle drive shaft, deviates from the value of actual necessity, becomes cogging and the remarkable existence of axle drive shaft 600.According to the related power-transfer clutch fault CVT pattern of step S212 of having appended control square frame B22; When the influence with respect to the clutch friction load torque Tc of the through torque Tep of driving engine was excluded, through torque Tep was consistent with the working control value for the driving engine of calculating.Its result, MG2 torque Tm can not deviate from necessary amount, has suppressed the cogging of axle drive shaft 600.When execution in step S212 or step S211, handle and to transfer to step S206, carry out selection repeatedly based on the speed change pattern of the best of system effectiveness.Variable speed control is carried out as above-mentioned.
In addition, in block scheme shown in Figure 17, the control square frame B22 that appends, if clutch friction load torque Tc is zero, then with Figure 16 the block scheme of illustrative common CVT pattern consistent.Therefore, also can always make the action of CVT pattern according to block scheme shown in Figure 17.
At this, carry out supplemental instruction to the comparison of the system effectiveness among the step S206 and based on the selection of the speed change pattern of this comparative result with reference to Figure 18.At this, Figure 18 is the action alignment chart of hybrid drive 30.In addition, in the figure, the position with Fig. 4 repetition is marked identical Reference numeral and suitably omits its explanation.
In Figure 18, Figure 18 (a) and MG1 are in that the situation of just changeing the zone is corresponding, and the CVT pattern is represented in the left side, and fixedly speed change pattern is represented on the right side.In the CVT pattern, that kind as described before is because the operating point of driving engine 200 is controlled in best burnup operating point; So the heat efficiency η e of driving engine 200 is good, because the influence of clutch friction load torque Tc; The generating torque is that MG1 torque Tg reduces, and the electric power revenue and expenditure of battery 12 worsens.When motor torque Te was risen, fuel discharge increased and causes burnup to worsen.
On the other hand, selecting fixedly under the situation of speed change pattern, such shown in the diagram dotted line, the operating point of driving engine 200 changes from the operating point (bullet) that gives best burnup.Thereby, comparing with the CVT pattern, the heat efficiency η e of driving engine 200 reduces, and system effectiveness η sys reduces.The each all reduction amounts of the reduction amount system effectiveness that reduction causes with heat efficiency of the system effectiveness that causes of the deterioration of this electric power revenue and expenditure relatively of ECU100, the speed change pattern that selective system efficient is higher.In addition, this with Figure 18 (b) illustrative MG1 to be in the situation of negative commentaries on classics state also identical.
< the 4th embodiment >
In above-mentioned the 3rd embodiment, use be the structure that when hybrid drive 30 adopts fixing speed change pattern, locks MG1 (accurately, locking MG1) via sun gear S1 and cam 910., the structure of the hybrid drive when obtaining fixing speed change pattern is not limited to such MG1 and locks.At this, the structure of other hybrid drive is described with reference to Figure 19.At this, Figure 19 is the summary pie graph that the structure of the hybrid drive 40 that the 4th embodiment of the present invention is related represented in summary.In addition, in the figure, the position with Figure 11 repetition is marked identical Reference numeral and suitably omits its explanation.
In Figure 19, hybrid drive 40 at alternate power division mechanism 300 and possess on power division mechanism 800 these aspects as another example of " Poewr transmission mechanism " involved in the present invention, constitutes different with hybrid drive 30.Power division mechanism 800 is as the modified roll mechanism that is made up of a plurality of rotating elements, employing be the mode of so-called cured civilian Nao formula sun and planet gear of second sun and planet gear 820 that possesses first sun and planet gear 810 and the double-pinion type of single pinion type.
First sun and planet gear 810 possesses sun gear 811, pinion carrier 812 and gear ring 813, also have the axis direction rotation and by pinion carrier 812 certainly then revolution remain in pinion carrier 812 with sun gear 811 and gear ring 813 ingear miniature gearss 814; Constituting sun gear 811 is connected with the rotor of dynamotor MG1; Pinion carrier 812 is connected with input shaft 500, and gear ring 813 is connected with axle drive shaft 600 in addition.
Second sun and planet gear 820 possesses sun gear 821, pinion carrier 822 and gear ring 823, also have the axis direction rotation and by pinion carrier 822 certainly then revolution ground remain in pinion carrier 822 respectively with sun gear 821 ingear miniature gearss 825 and with gear ring 823 ingear miniature gearss 824, constitute sun gear 821 and be connected with the cam 910 (not shown) of lockout mechanism 900.That is, in this embodiment, sun gear 821 plays a role as another example of " first rotating element " involved in the present invention.
Like this; Power division mechanism 800 possesses as a whole: the sun gear 821 (first rotating element) of the sun gear 811 of first sun and planet gear 810, second sun and planet gear 820, the first rotating element group that is made up of the gear ring 823 of the pinion carrier 812 of interconnective first sun and planet gear 810 and second sun and planet gear 820, the second rotating element group that also has the pinion carrier 822 by the gear ring 813 of interconnective first sun and planet gear 810 and second sun and planet gear 820 to constitute amount to four rotating elements.
According to hybrid drive 40; When center gear 821 becomes lock-out state, when its rotative speed becomes zero, stipulates the i.e. rotative speed of the first rotating element group of a remaining rotating element by the second rotating element group that has with the unique cooresponding rotative speed of speed V with this sun gear 821.Constitute the pinion carrier 812 of the first rotating element group; Owing to be connected with the input shaft 500 of the bent axle 205 that is connected in driving engine 200 (not shown); As a result, the combustion engine rotative speed NE of driving engine 200 becomes and the unique corresponding relationship of speed V, has realized fixedly speed change pattern.Like this, fixedly speed change pattern also can be achieved in the structure beyond the hybrid drive 40, and with it accordingly, the lock object of lockout mechanism 900 also can suitably change.In a word, the drive controlling of the best of the drag torque calculated of the calculating of the drag torque in the lockout mechanism 900 and consideration can be same with the 3rd embodiment.
The present invention is not limited to above-mentioned embodiment; In the scope of design of not violating the invention of understanding according to claims and description in its entirety or thought, can suitably change, the subsidiary in addition control setup of the motor vehicle driven by mixed power of change like this is also contained in the technical scope of the present invention.
Industrial applicibility
The present invention is applicable to can be in stepless shift mode and fixedly switch the motor vehicle driven by mixed power of speed change pattern between the speed change pattern.
Description of reference numerals
1... motor vehicle driven by mixed power, 10... hybrid drive, 20... hybrid drive, 30... hybrid drive; 40... hybrid drive, 100...ECU, 200... driving engine, 201... cylinder; 203... piston, 205... bent axle, 300... power division mechanism, MG1... dynamotor; MG2... dynamotor, 400... stop mechanism, 500... input shaft, 600... axle drive shaft; 700... speed reduction gearing, 800... power division mechanism, 900... lockout mechanism.

Claims (14)

1. the control setup of a motor vehicle driven by mixed power, the control setup of this motor vehicle driven by mixed power is controlled motor vehicle driven by mixed power,
Said motor vehicle driven by mixed power possesses:
Dynamical element comprises rotating machine and combustion engine,
Poewr transmission mechanism; Possess can mutual differential rotation a plurality of rotating elements; Said a plurality of rotating element comprise can by first rotating element of said rotating machine adjustment rotative speed, be connected with axle drive shaft that axletree links to each other on second rotating element and be connected on the said combustion engine the 3rd rotating element and
Lockout mechanism can switch the state of said first rotating element between lock-out state that can not rotate and the unlock state that can rotate,
Said motor vehicle driven by mixed power constitutes with the mode of can be in stepless shift mode and fixedly switching speed change pattern between the speed change pattern; Wherein, Under said stepless shift mode, as the rotative speed of said combustion engine and the converter speed ratio continuous variable of the ratio of the rotative speed of said axle drive shaft, and the situation that is in said unlock state with said first rotating element is corresponding; Under said fixedly speed change pattern; Said converter speed ratio is fixed, and the situation that is in said lock-out state with said first rotating element is corresponding
The control setup of said motor vehicle driven by mixed power is characterised in that,
The control setup of said motor vehicle driven by mixed power possesses:
Operation condition is confirmed the unit, confirm said dynamical element operation condition and
Judging unit, this judging unit is judged having or not of drag torque in the said lockout mechanism based on determined said operation condition.
2. the control setup of motor vehicle driven by mixed power as claimed in claim 1 is characterized in that,
The torque that said operation condition is confirmed to confirm said rotating machine according to the controlling quantity of said rotating machine in the unit is as first torque; This first torque is as a said operation condition; And; The torque of confirming said rotating machine according to the operating condition of the said motor vehicle driven by mixed power relevant with the torque of said rotating machine is as second torque, and this second torque is as another said operation condition
Said judging unit is judged having or not of said drag torque based on determined said first torque and said second torque.
3. the control setup of motor vehicle driven by mixed power as claimed in claim 2 is characterized in that,
When said rotating machine is in when just changeing state, under the big situation of determined said second torque of determined said first torque ratio, and
When said rotating machine is in negative commentaries on classics state, under the little situation of said second torque of determined said first torque ratio,
Said judging unit is judged as respectively and produces said drag torque.
4. the control setup of motor vehicle driven by mixed power as claimed in claim 1 is characterized in that,
Said operation condition confirm the unit confirm at least one side in said rotating machine and the said combustion engine to the convergence state of target rotational speed convergence as said operation condition,
Said judging unit is judged having or not of said drag torque based on the said convergence state of confirming.
5. the control setup of motor vehicle driven by mixed power as claimed in claim 1 is characterized in that,
The control setup of said motor vehicle driven by mixed power also possesses first control unit, and this first control unit is controlled said rotating machine with the mode that reduces with the cooresponding counter-force torque of the torque of said combustion engine during stable the going of said motor vehicle driven by mixed power,
Said operation condition confirm that the unit is confirmed to follow said counter-force torque to reduce and the variable quantity of the rotative speed of the said combustion engine that produces as said operation condition,
Said judging unit is judged having or not of said drag torque based on the variable quantity of the rotative speed of the determined said said combustion engine of following said counter-force torque to reduce and producing.
6. the control setup of motor vehicle driven by mixed power as claimed in claim 1 is characterized in that,
The variable quantity of the rotative speed of the said combustion engine when said operation condition confirms that starting is confirmed in the unit is as said operation condition,
Said judging unit is judged having or not of said drag torque based on the variable quantity of the rotative speed of the said combustion engine in determined said when starting.
7. the control setup of motor vehicle driven by mixed power as claimed in claim 1 is characterized in that,
The control setup of said motor vehicle driven by mixed power possesses:
Side-play amount is confirmed the unit, is being judged as under the situation that produces said drag torque, the operation condition of the said dynamical element of confirming to cause because of said drag torque with respect to the side-play amount of the operation condition under the normal circumstances and
Second control unit, corresponding determined said side-play amount is controlled the starting torque of said combustion engine and at least one side who reduces in the torque.
8. the control setup of motor vehicle driven by mixed power as claimed in claim 4 is characterized in that, possesses:
The 3rd control unit; Under the state of having selected said stepless shift mode; With the rotative speed of said rotating machine mode to said target rotational speed convergence, the rotative speed of corresponding said rotating machine and the deviation of said target rotational speed control said rotating machine torque and
Calculate the unit; The inertia torque value that produces because of the inertia of the rotatory inertia system that comprises said dynamical element during the said rotating machine of the torque value of feedback of the said rotating machine of calculating when being based on the said rotating machine of corresponding said deviation control and corresponding said deviation control is calculated said drag torque.
9. the control setup of motor vehicle driven by mixed power as claimed in claim 8 is characterized in that,
The control setup of said motor vehicle driven by mixed power also possesses identifying unit, and this identifying unit is judged the state of said lockout mechanism based on the said drag torque of being calculated.
10. the control setup of motor vehicle driven by mixed power as claimed in claim 9 is characterized in that,
Said identifying unit is to be judged to be said lockout mechanism under the situation more than the specified value to be in faulty condition in the said drag torque of being calculated.
11. the control setup of motor vehicle driven by mixed power as claimed in claim 8 is characterized in that,
The control setup of said motor vehicle driven by mixed power also possesses amending unit, and the corresponding said drag torque of being calculated of this amending unit is revised the output torque of said axle drive shaft.
12. the control setup of motor vehicle driven by mixed power as claimed in claim 8 is characterized in that,
The control setup of said motor vehicle driven by mixed power also possesses selected cell, and this selected cell is selected the side in said stepless shift mode and the said fixedly speed change pattern based on the said drag torque of being calculated.
13. the control setup of motor vehicle driven by mixed power as claimed in claim 12 is characterized in that,
Said selected cell is selected the high side of system effectiveness in said stepless shift mode and the said fixedly speed change pattern, said motor vehicle driven by mixed power.
14. the control setup of motor vehicle driven by mixed power as claimed in claim 8 is characterized in that,
Said motor vehicle driven by mixed power also possess can with said axle drive shaft between carry out power input and output and other rotating machines different with said rotating machine.
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